急!SELECT Brand, Model, FROM INVENTERY WHERE (Model LIKE '*[?]*')不工作

orangeroad 2004-07-11 08:52:37
在VB。NET中的QUERY BUILDER写
SELECT Brand, Model, FROM INVENTERY WHERE (Model LIKE '*[?]*')
无法运行。
SELECT Brand, Model, FROM INVENTERY WHERE (Model LIKE ?)
可以运行,但是全部满足

应该怎样写 查询 部分 满足条件
多谢大侠
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junki 2004-10-15
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LIKE MATCH


数值型的时候,才不加单引号啊
orangeroad 2004-07-11
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仍然不行,因为我是把SQL写在 CONFIGURE DATA ADAPTER ==>> QUERY BUILDER 中
让VB 和ACCESS 连接

MATCH 全部可以工作, 但是为什么部分MATCH不行呢
一事無成 2004-07-11
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SELECT Brand, Model FROM INVENTERY WHERE (Model LIKE '%[?]%')
SQL中模糊匹配用%
mmcgzs 2004-07-11
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SELECT Brand, Model FROM INVENTERY WHERE (Model LIKE '%[?]%')
hhjjhjhj 2004-07-11
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LIKE '%[?]%'
试试
饮水需思源 2004-07-11
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SELECT Brand, Model FROM INVENTERY WHERE (Model LIKE '%[?]%')

在最在一个字段与from之间不能有逗号,SQL中模糊匹配用%
WELCOME TO TURBO C 2.01 ----------------------- This README file contains important, last minute information about Turbo C 2.01. The HELPME!.DOC file on the COMPILER/UTILITIES disk also answers many common Technical Support questions. TABLE OF CONTENTS ----------------- 1. How to Get Help 2. Installation 3. Important Notes 4. Additional Notes 5. Notes for Turbo Prolog Users 6. Files on the Disks 1. HOW TO GET HELP ------------------- If you have any problems, please read this file, the HELPME!.DOC file, and the Turbo C manuals first. If you still have a question and need assistance, help is available from the following sources: 1. Type GO BOR on the CompuServe bulletin board system for instant access to the Borland forums with their libraries of technical information and answers to common questions. If you are not a member of CompuServe, see the enclosed special offer, and write for full details on how to receive a free IntroPak containing a $15 credit toward your first month's on- line charges. 2. Check with your local software dealer or users' group. 3. Write to us at the following address: Borland International Turbo C Technical Support 1800 Green Hills Road P.O. Box 660001 Scotts Valley, CA 95066-0001 Please remember to include your serial number or we will be unable to process your letter. 4. If you have an urgent problem that cannot wait and you have sent in the license agreement from the front of your manual, you may call the Borland Technical Support Department at (408) 438-5300. Please have the following information ready before calling: a. Product name and serial number on your original distribution disk. Please have your serial number ready or we will be unable to process your call. b. Product version number. The version number for Turbo C is displayed when you first load th
WELCOME TO TURBO C 2.0 ---------------------- This README file contains important, last minute information about Turbo C 2.0. The HELPME!.DOC file on the COMMAND LINE/UTILITIES disk also answers many common Technical Support questions. TABLE OF CONTENTS ----------------- 1. How to Get Help 2. Installation 3. Important Notes 4. Corrections to the Manuals 5. Additional Notes 6. Notes for Turbo Prolog Users 7. Files on the Disks 1. HOW TO GET HELP ------------------- If you have any problems, please read this file, the HELPME!.DOC file, and the Turbo C manuals first. If you still have a question and need assistance, help is available from the following sources: 1. Type GO BOR on the CompuServe bulletin board system for instant access to the Borland forums with their libraries of technical information and answers to common questions. If you are not a member of CompuServe, see the enclosed special offer, and write for full details on how to receive a free IntroPak containing a $15 credit toward your first month's on- line charges. 2. Check with your local software dealer or users' group. 3. Write to us at the following address: Borland International Turbo C Technical Support 1800 Green Hills Road P.O. Box 660001 Scotts Valley, CA 95066-0001 Please remember to include your serial number or we will be unable to process your letter. 4. If you have an urgent problem that cannot wait and you have sent in the license agreement from the front of your manual, you may call the Borland Technical Support Department at (408) 438-5300. Please have the following information ready before calling: a. Product name and serial number on your original distribution disk. Please have your serial number ready or we will be unable to process your call. b. Product version number. The version number for Turbo C is displayed when you first load the program and before you press any keys. c. Computer brand, model, and the brands and model numbers of any additional hardware. d. Operating system and version number. (The version number can be determined by typing VER at the MSDOS prompt.) e. Contents of your AUTOEXEC.BAT file. f. Contents of your CONFIG.SYS file. 2. INSTALLATION ---------------- The INSTALL/HELP disk contains a program called INSTALL.EXE that will assist you with the installation of Turbo C 2.0. There are three options for installation: 1. Hard Disk - This option allows you to pick the subdirectories where the files will be loaded. It will create a TURBOC.CFG file based on those directories. 2. Update from TC 1.5 - This allows for an easy update from version 1.5. After the files are copied, all the installed options from your current TC.EXE will be transferred to the new one. This is especially useful if you have modified the colors or editor keys. 3. Floppy Disk - This option will build either a command line or Integrated Development Environment version for a two drive system. Be sure to have three formatted disks ready before you start. To start the installation, change your current drive to the one that has the install program on it and type INSTALL. You will be given instructions in a box at the bottom of the screen for each prompt. For example, if you will be installing from drive A:, type: A: INSTALL You should read the rest of this README file to get further information about this release before you do the installation. 3. IMPORTANT NOTES ------------------- o The file HELPME!.DOC contains discussions of common questions and answers concerning Turbo C 2.0. You should consult it for answers to problems that aren't covered in this file or in the manuals. o If you are running INSTALL or TCINST on a laptop or any other system that uses an LCD or composite display, you should set your system to black and white mode before running INSTALL or TCINST. You can do this from DOS with the following command line: mode bw80 or, you can force INSTALL or TCINST to come up in black and white mode by using the /b switch: tcinst /b o /P PARAMETER FOR TC.EXE. A new command-line switch controls palette swapping on EGA video adapters. Using this switch tc /p hello is recommended only when the user program modifies the EGA palette registers. When /P is specified, the EGA palette will be restored each time the screen is swapped. In general, you don't need to use this switch unless your program modifies the EGA palette registers, or unless your program uses BGI to change the palette. o A program that takes over interrupt 9 cannot be debugged with the integrated debugger. Use the standalone Turbo Debugger instead. o exec() WITH NOVELL NETWORK. Versions of the Novell network system software earlier than 2.01-2 do not support a DOS call used by exec(), spawn(), and system(). If you are using the Integrated Development Environment to run a program that uses any of these functions and you have early Novell system software, run the program from DOS. To do this from the Integrated Development Environment you can use Alt-F/O. o If you used the INSTALL program to upgrade from version 1.5, or if you used CINSTXFR to transfer options from an installation of version 1.5, check the setting of the standard stack frame option in the Integrated Development Environment (Alt-O/C/C/S). If you are going to use the integrated debugger this option should be turned ON. o If you are having problems with the call stack or qualified names, make sure you have compiled with the standard stack frame option turned on. o The ANSI draft has changed the syntax of labels. A label now must always be followed by a statement. This means that code like this is no longer accepted: { . . . jump_label: } If you have code like this, change it to look like this: { . . . jump_label: ; /* need a statement here! */ } o TCC has a switch to specify which assembler to look for. By default, it will look for TASM.EXE. If you want to use a different assembler, use -E, as described in the Reference Guide. o When using THELP on an AT&T 6300, be sure to use the /L25 command-line option, as described in the file THELP.DOC. o When you use qualified variable names as described on page 57 of the User's Guide you don't need to use the module name to access a variable that is local to a global function. The module name is only needed when you access a static variable or a variable that is local to a static function. o Because of the limited memory available in the Tiny model, it no longer supports graphics functions. o The Version 1.5 graphics drivers (*.BGI) are not compatible with the Version 2.0 graphics library. Use the graphics drivers distributed with Version 2.0. o When used with a Zenith Z-449 card, the BGI autodetection code will always select the 640X480 enhanced EGA mode. If you are using the Z-449 with a monitor that is not compatible with this mode, it will be necessary to override the GraphDriver and GraphMode parameters used in the BGI initgraph() call. 4. CORRECTIONS TO THE MANUALS ------------------------------ REFERENCE GUIDE: Page 159 The prototype for the function getdefaultpallette() is incorrect. It should be struct palettetype * far _Cdecl getdefaultpalette( void ); USER'S GUIDE: Page 57 In the section entitled "Qualifying Variable Names," the last sentence should read "...need to type only myfunc.myvar." 66 The directions for compiling the WORDCNT program are incorrect. There is no WORDCNT.PRJ file; all you need to do is load the file WORDCNT.C into the editor. Once you have done that, the rest of the instructions are correct. 5. ADDITIONAL NOTES -------------------- 5.1 NOTES FOR VERSION 1.0 & 1.5 USERS ------------------------------------- o You must use the Version 2.0 libraries with the 2.0 compilers. o The Integrated Development Environment no longer displays the message "Press any key to return to Turbo C..." when your program terminates. Instead, at the end of your program the User screen is replaced by the Integrated Development Environment. To view the User screen, press Alt-F5 or select Alt-R/S. When you are viewing the User screen, pressing any key will return you to the Integrated Development Environment. o A new pseudo-variable has been added. _FLAGS now contains the value of the flags register so you can test the flags at any point in your program. o The ssignal() and gsignal() functions are no longer supported. See the section in this README on how to convert programs that use them. o The cprintf() function now works as documented. It does not translate line-feeds into CR/LF combinations. o Some compatibles had a problem under Version 1.5 because it used interrupt 18H. Version 2.0 does not use this interrupt, so you shouldn't encounter this problem anymore. o The program TCINST.COM in Version 1.0 has been changed to an .EXE file. You should delete the TCINST.COM program before trying to run the new TCINST.EXE. Otherwise, MS-DOS will actually run the old one. o The FILE structure for streams in Version 1.0 (but not 1.5) has been changed, so that the function tmpfile() could be implemented. You should recompile any modules that use stream I/O. 5.2 THELP ---------- THELP is a memory-resident utility program that gives you access to the Turbo C context-sensitive help system from any program. You don't need to use THELP if you're in the Integrated Development Environment, but it is especially useful if you use the command line compiler and your own text editor, or if you are debugging with the standalone Turbo Debugger. To use THELP, load THELP.COM into memory by typing at the DOS command line: thelp You activate ("pop-up") THELP by typing its hot key -- by default numeric keypad <5>. All Turbo C help commands apply (F1, Ctrl-F1, Alt-F1). For a complete description of THELP, refer to THELP.DOC in the Documentation Subdirectory. 5.3 USING CINSTXFR.EXE ---------------------- Your Turbo C 2.0 package contains a program named CINSTXFR.EXE, which can be used to transfer the configuration of the Integrated Development Environment from your copy of Turbo C 1.5 (not for 1.0) to your new installation of Turbo C 2.0. This program is run automatically by INSTALL.EXE if you select the option to "Update Hard Drive Copy of Turbo C 1.5 to Turbo C 2.0." If you prefer to do this yourself, you can run CINSTXFR.EXE from the DOS command line. CINSTXFR.EXE takes two arguments: the first is the name of your Turbo C 1.5 Integrated Development Environment file (usually TC.EXE), and the second is the name of your Turbo C 2.0 Integrated Development Environment file (also usually TC.EXE). Either one of these names can also include a path name. For example, if your copy of the Turbo C 1.5 Integrated Development Environment file is named TC.EXE and is in a directory named \TURBOC and your copy of the Turbo C 2.0 Integrated Development Environment file is also named TC.EXE but is located in a directory named \TC2, the command line to copy the configuration from 1.5 to 2.0 would look like this: CINSTXFR \TURBOC\TC.EXE \TC2\TC.EXE This will transfer all the options that you installed in your copy of Turbo C 1.5 to your copy of Turbo C 2.0. CINSTXFR.EXE does not work with Turbo C 1.0. If you are upgrading from Turbo C 1.0, you will have to install the options yourself. 5.4 CHANGED SWITCHES FOR OBJXREF -------------------------------- OBJXREF is an object module cross reference utility and is described on page 528 of the Turbo C Reference Guide. The /O option (object files directory) has been changed to the /D (directories) option. The switch now allows for multiple search directories to be specified. The new syntax is: OBJXREF /Ddir1[;dir2[;dir3]] or OBJXREF /Ddir1 [/Ddir2] [/Ddir3] OBJXREF will search each of the directories in the specified order for all object and library files. If no /D option is used, only the current directory will be searched. However, if a /D option is used, the current directory will NOT be searched unless it is included in the directory list. For example, to first search the BORLAND directory for files and then search the current directory, you would type OBJXREF /Dborland;. If multiple search directories are specified and a file matching the file specification is found, OBJXREF will include the file as part of the cross-reference. OBJXREF will only continue to search the other directories for the same file specification if the file specification contains wildcards. A new option has been added to allow you to specify an output file where OBJXREF will send any reports generated. The new option is the /O option, and has the following syntax: OBJXREF myfile.obj /RU /Ofilename.ext By default, all output is sent to the console. 5.5 CONVERSION INFORMATION FOR ssignal() AND gsignal() ------------------------------------------------------ Note: The C library and SIGNAL.H no longer support the ssignal() and gsignal() functions. ssignal() and gsignal() were from the old UNIX System III days. The ANSI standard no longer supports them nor does the current UNIX System V Interface Definition specification. To ease portation problems for people moving older code to Turbo C, we supply the source for the functions that came with TC 1.0 and TC 1.5. Also, the following discussion describes how code can be converted to do the same sort of things that ssignal() and gsignal() do without actually using them. NOTE: The constants defined in SIGNAL.H for SIG_IGN and SIG_DFL are different from the constants that were in TC 1.0 and TC 1.5. By using a globally declared array of function pointers, you can simulate the actions of ssignal() and gsignal() by using the following macros. Notice how the global table entry [0] is used as a temporary variable in the ssignal macro allowing the macro to swap the values and still return the original one. int (*_sigTable[16]) = { SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, SIG_IGN, }; #define ssignal(num, action) \ ( \ (((num) < 1) || ((num) > 15)) ? SIG_DFL : \ ( \ (_sigTable[0] = _sigTable[(num)]), /* List of actions */ \ _sigTable[(num)] = (action), /* The last expression */ \ _sigTable[0] /* is the return value */ \ ) \ ) \ #define gsignal(num) \ ( \ (((num) < 1) || ((num) > 15)) ? 0 : \ ( \ (_sigTable[(num)] == SIG_IGN) ? 1 : \ ( \ (_sigTable[(num)] == SIG_DFL) ? 0 : (*_sigTable[(num)])() \ ) \ ) \ ) \ 6. NOTES FOR TURBO PROLOG USERS -------------------------------- o If you are linking C code with programs generated by Turbo Prolog 2.0, use the file INIT.OBJ provided on the EXAMPLES/BGI/MISC disk of the Turbo C 2.0 package instead of the file provided with Turbo Prolog 2.0. There have been some changes made in Turbo C 2.0 that require the use of this new file. o If your C code uses floating point math and you link with the emulator library, Prolog will not automatically detect a math coprocessor chip. If you want to force the program to use the coprocessor, link it with FP87.LIB instead of EMU.LIB. 7. FILES ON THE DISKS ---------------------- INSTALL/HELP ------------ INSTALL EXE - Installation program README COM - Reads this README TCHELP TCH - Help file for Turbo C THELP COM - Pop-up utility to access TCHELP.TCH THELP DOC - Documentation for THELP.COM README - This file INTEGRATED DEVELOPMENT ENVIRONMENT ---------------------------------- TC EXE - Turbo C Compiler TCCONFIG EXE - Program to convert configuration files MAKE EXE - Program for managing projects GREP COM - Turbo GREP program TOUCH COM - Program that updates a file's date and time COMMAND LINE/UTILITIES ---------------------- TCC EXE - Command-line version of Turbo C Compiler CPP EXE - Turbo C preprocessor TCINST EXE - Installation program for TC.EXE TLINK EXE - Borland Turbo Linker HELPME! DOC - Common questions and answers LIBRARIES --------- C0S OBJ - Small model startup code C0T OBJ - Tiny model startup code C0L OBJ - Large model startup code MATHS LIB - Small model math library MATHL LIB - Large model math library CS LIB - Small model run-time library CL LIB - Large model run-time library EMU LIB - 8087 emulator library GRAPHICS LIB - Graphics library FP87 LIB - 8087 library TLIB EXE - Borland Turbo Librarian HEADER FILES/LIBRARIES ---------------------- ???????? H - Turbo C header files - Subdirectory with SYS\*.H header files C0C OBJ - Compact model startup code C0M OBJ - Medium model startup code MATHC LIB - Compact model math library MATHM LIB - Medium model math library CC LIB - Compact model run-time library CM LIB - Medium model run-time library EXAMPLES/BGI/MISC ----------------- UNPACK COM - Program to unpack the .ARC files OBJXREF COM - Object file cross-reference utility C0H OBJ - Huge model startup code MATHH LIB - Huge model math library CH LIB - Huge model run-time library GETOPT C - Parses options in command line HELLO C - Example Turbo C program MATHERR C - Source code for handling math library exceptions SSIGNAL C - Source code for ssignal and gsignal functions CINSTXFR EXE - Program to copy TC 1.5 installation to TC 2.0 INIT OBJ - Initialization code for use when linking with Prolog BGI ARC - BGI drivers and fonts BGIOBJ EXE - Conversion program for fonts and drivers ATT BGI - Graphics driver for ATT400 graphics card CGA BGI - Graphics driver for CGA EGAVGA BGI - Graphics driver for EGA and VGA HERC BGI - Graphics driver for Hercules IBM8514 BGI - Graphics driver for IBM 8514 graphics card PC3270 BGI - Graphics driver for PC3270 GOTH CHR - Font for gothic character set LITT CHR - Font for small character set SANS CHR - Font for sans serif character set TRIP CHR - Font for triplex character set BGIDEMO C - Graphics demonstration program STARTUP ARC - ARC file with startup source code and related files RULES ASI - Assembler include file for interfacing with Turbo C C0 ASM - Assembler source for startup code SETARGV ASM - Assembler source code for parsing the command line SETENVP ASM - Assembler source code for preparing the environment BUILD-C0 BAT - Batch file for building the startup code modules MAIN C - Alternative, stripped-down C main file EMUVARS ASI - Assembler variable declarations for emulator WILDARGS OBJ - Object code for module to expand wildcard arguments EXAMPLES ARC - Various C examples code CPASDEMO PAS - Pascal program that demonstrates Turbo Pascal 4.0 - Turbo C interface CPASDEMO C - C example module for the Turbo Pascal 4.0 - Turbo C interface demonstration CTOPAS TC - Configuration file for use with TC.EXE that creates Turbo C modules in the correct format for linking with Turbo Pascal 4.0 programs CBAR C - Example function to be used with PBAR.PRO PBAR PRO - Example Turbo Prolog program demonstrating interface with Turbo C WORDCNT C - Example program demonstrating source level debugging. NOTE: DO NOT RUN THIS PROGRAM WITHOUT READING THE DISCUSSION IN THE MANUAL. IT CONTAINS DELIBERATE ERRORS. WORDCNT DAT - Data file for use by WORDCNT.C MCALC ARC - Mcalc sources and doc MCALC DOC - MicroCalc documentation MCALC C - MicroCalc main program source code MCINPUT C - MicroCalc input routines source code MCOMMAND C - MicroCalc commands source code MCPARSER C - MicroCalc input parser source code MCUTIL C - MicroCalc utilities source code MCDISPLY C - MicroCalc screen display source code MCALC H - The header file for MicroCalc MCALC PRJ - The MicroCalc project file
Welcome to Turbo C++ Version 3.0 -------------------------------- This README file contains important information about Turbo C++. For the latest information about Turbo C++ and its accompanying programs and manuals, read this file in its entirety. TABLE OF CONTENTS ----------------- 1. How to Get Help 2. Installation 3. Features 4. Important Information 5. Testing Your Expanded Memory 6. Corrections to the On-line Help 1. HOW TO GET HELP ------------------- If you have any problems, please read this file, the HELPME!.DOC and other files in your DOC subdirectory, and the Turbo C++ manuals first. If you still have a question and need assistance, help is available from the following sources: 1. Type GO BPROGB on the CompuServe bulletin board system for instant access to the Borland forums with their libraries of technical information and answers to common questions. If you are not a member of CompuServe, see the enclosed special offer, and write for full details on how to receive a free IntroPak containing a $15 credit toward your first month's on-line charges. 2. Check with your local software dealer or users' group. 3. Borland's TECHFAX service. Call (800) 822-4269 for a FAX catalog of entries. 4. If you have an urgent problem that cannot wait and you have sent in the license agreement that came with the package, you may call the Borland Technical Support Department at (408) 438-5300. Please have the following information ready before calling: a. Product name and serial number on your original distribution disk. Please have your serial number ready or we will be unable to process your call. b. Product version number. The version number for Turbo C++ can be displayed by pressing Alt-H/A. c. Computer brand, model, and the brands and model numbers of any additional hardware. d. Operating system and version number. (The version number can be determined by typing VER at the DOS prompt.) e. Contents of your AUTOEXEC.BAT file. f. Contents of your CONFIG.SYS file. 2. INSTALLATION ---------------- You MUST use the INSTALL program to install Turbo C++. The files on the distribution disks are all archived and have to be properly assembled. You cannot do this by hand! IMPORTANT! If you want to create backup copies of your disks, make sure that you put the backup on the same type of disk as the source. If you're backing up the 5 1/4 inch 1.2 Mb disk set, use only blank 5 1/4 inch 1.2 Mb disks for backup, etc. The installation will not work correctly if you do not use the same media type for the backup disks. To start the installation, change your current drive to the one that has the install program on it and type INSTALL. You will be given instructions in a box at the bottom of the screen for each prompt. For example, if you will be installing from drive A:, type: A: INSTALL - This INSTALL handles the installation of both the compiler and tools in one operation, and allows several new configuration options. - After installation, make sure you insert \TC\BIN - or whatever you selected as your BIN directory - into your DOS path so the executable files can be found. - Note: The list of files is contained in a separate file called FILELIST.DOC, which will appear in the target directory you specify during installation. - After your initial installation, you can run INSTALL again to add elements you omitted the first time. Just select the items you want to add in the INSTALL options screen. Because some things you may want to save could be overwritten, review the following items to make sure you don't lose important information: 1. Selecting CMD (the Command-line compiler) causes an overwrite of any existing turboc.cfg & tlink.cfg file with path information provided in that INSTALL session. Any switches other than -L (library path) and -I (include path) will not be preserved. 2. Selecting IDE will reset the include and library paths to those provided in that INSTALL session. 3. By selecting any one of the following, the help file paths and choices for THELP.CFG will reflect the current session's installation choices: a. CMD - command-line compiler b. IDE - integrated environment 4. Alterations to headers or startup files will be overwritten if any library models are selected. In general, any selection you make of something installed earlier will cause an overwrite of the earlier version without prompting. You should read the rest of this README file to get further information about this release before you do the installation. 3. FEATURES ------------ Turbo C++ 3.0 includes big speed and capacity gains. Here are some important features found in this version: - DPMI services for increased capacity - C++ 2.1 support, including the new nested class specifications, and support of C++ 3.0 templates. - Support for pre-compiled headers for substantial time savings during subsequent recompiles. - Color syntax highlighting - Unlimited Undo/Redo replacing previous 'restore line' capability - Added library functions for compatibility with other runtime libraries, and addition of support for long double parameters in math functions. (Please refer to On-line Help for details.) - New MAKE features. (Please see the MAKE chapter in the User's Guide for details.) - Added BGI (Borland Graphics Interface) fonts and support. (See "New BGI fonts" below.) - A resident DPMI kernel program, DPMIRES.EXE. (See "DPMI" below.) - THELP now allows you to switch between help files without unloading and reloading. (Please see UTIL.DOC for details.) NEW BGI FONTS ------------- Several new fonts have been added to the Borland Graphics Interface: Name Value Description ------------------------------------------- SCRIPT_FONT 5 Stroked script font SIMPLEX_FONT 6 Stroked simplex font TRIP_SCR_FONT 7 Stroked triplex script font COMPLEX_FONT 8 Stroked complex font EURO_FONT 9 Stroked European font BOLD_FONT 10 Stroked bold font The fonts in the BGI now support the full ASCII character set. DPMI ---- TC.EXE, TCC.EXE, and TLINK.EXE are now hosted under DPMI. These files support protected-mode compilation and replace the files of the same name in Turbo C++ Second Edition. Turbo C++ Second Edition should continue to be used in instances where real-mode compilation is desired. If you encounter a "machine not in database" message while attempting to run the compiler, run the DPMIINST program to add your machine configuration to the DPMI server database. This version includes a resident DPMI host program, DPMIRES.EXE, that allows you to preload the server before invoking TC, TCC, or any other DPMI-hosted executables. If you want to run such hosted EXEs in a Windows Standard Mode DOS window, you should run DPMIRES.EXE before loading Windows. To do this, enter the following commands at DOS: set DPMIMEM=MAXMEM 2000 dpmires win /s If you want to limit the amount of extended memory used by the DPMI-hosted executables, an environment variable called DPMIMEM can be set to do so. For instance, the command set DPMIMEM=MAXMEM 2000 reserves about 2 Mb of memory for DPMIRES. The number after MAXMEM can be adjusted, but cannot be lower than 1000. The hosted executables cannot spawn each other when SHARE is loaded. For instance, if you run MAKE on a file which in turn calls MAKE again, you will get a sharing violation. In this specific case, you can call the real mode version, MAKER, within the given makefile, and a sharing violation won't occur. 4. IMPORTANT INFORMATION ------------------------- - When using Brief with THELP, make sure to use Brief's -p switch to ensure that the thelp window will be visible. - We recommend that you use the following mouse drivers with this product: Microsoft Mouse version 7.04 or later; Logitech Mouse version 5.01 or later; Genius Mouse version 9.06 or later. - If you get a "floating point formats not linked" message at runtime, put the following somewhere in your source files: extern void _floatconvert(); #pragma extref _floatconvert This will force inclusion of floating point formats, which may not be linked to reduce executable size. COMPILER - The default extension for source files to the command-line compiler is .CPP; that is, if you enter TCC -c test the compiler will search for test.cpp, and give an error if a file of that name cannot be found. If you want to have the command-line compiler assume a .c extension and C language source, use the command-line option -P-c. For more information, see "The command-line compiler" in the User's Guide. - Note that the Generate COMDEFs choice under Options|Compiler|Advanced Code Generation and the -Fc command- line option are only supported in the C language. Linker errors will result if you attempt to use a communal variable in C++. - The macros min() and max() are not defined when stdlib.h is compiled as C++ (to allow their use in 3rd party libraries, etc.). - Note that SYMDEB creates .SYM files for use in debugging; Turbo C++ creates .SYM files for pre-compiled headers. They are not compatible and collisions should be avoided by setting the name of the pre-compiled header file (using - H=filename). - There is now full support of distance modifiers (near and far) used for class member pointers. Here are two sample declarations and their meanings: void (A::* far var) (); this is a far variable 'var' of type 'void (A::*)()'; void (far A::* var) (); this is a 'default distance' variable 'var' of type 'void (far A::*)()' - If you use C++ templates, and use a separate TLINK command line rather than letting TCC invoke TLINK, you should make sure that you turn on case-sensitive links with the /c switch. - Incorrect code will be generated if you have a statement of the type "A op B" where either A or B is an enum and the other operand is a long, and "op" is one of the following operators: += -= *= /= | ^ The same problem applies when the operands are a non-integer enum and an int. Cast the enum to long or int respectively to solve the problem. IDE - When debugging a mouse application the Options|Debugger|Display Swapping option should be set to "Always" for best results. - In the IDE, the mouse cursor is turned off during compilation for performance improvements. - To run or debug an overlaid application in the IDE when DOS SHARE is loaded, the .EXE file must first be marked as read-only. Otherwise, unload SHARE. - Pressing Control-Break twice while running or stepping a program from the IDE may cause unexpected results. In particular, avoid pressing Control-Break twice in response to any function requiring input (scanf, getch, etc.). To break out of a program during such interaction, press Control-Break and enter a valid input string. Control will be returned to the IDE. EXAMPLE PROGRAMS - When you are running any example programs that come with .PRJ files, if you didn't use the standard directories when you installed Turbo C++ you will have to change the .PRJ file to reflect your actual directory setup. Do this from inside Turbo C++ with Alt-O/D. LINKING C++ WITH C - Linking C++ modules with C modules requires the use of a linkage specification. Prototypes for C functions within C++ modules must be in one of the following forms: extern "C" declaration extern "C" { declarations } For example, if a C module contains these functions: char *SCopy(char*, char*); void ClearScreen(void) they must be declared in a C++ module in one of the following ways: extern "C" char *SCopy(char*, char*); extern "C" void ClearScreen(void); or extern "C" { char *SCopy(char*, char*); void ClearScreen(void); } Failure to do so will result in "Undefined symbol" errors during link. For further examples, see the standard header files. CLASS LIBRARY - Two versions of the class libraries are provided; one that includes debug information and one that does not. Small versions of each are provided, and project files are provided to build other models. Note that the non-debug versions are used by default. If you would like to use the debug version, copy it to the non-debug file. For instance, in the CLASSLIB\LIB directory, copy TCLASDBS.LIB to TCLASSS.LIB for the small model version. - In some places the User's Guide incorrectly refers to the online documentation for the Container Class Libraries as CONTAIN.DOC. The correct file name is CLASSLIB.DOC, located in the ..\DOC directory. 5. TESTING YOUR EXPANDED MEMORY: EMSTEST.COM --------------------------------------------- Included with Turbo C++ is a program to test your Expanded Memory hardware and software. If you have problems using Turbo C++ with your EMS, type EMSTEST at the DOS prompt and follow the instructions. 6. CORRECTIONS TO THE ON-LINE HELP ----------------------------------- The information for alloca is not available in on-line help. The correct help screen should read as follows: ------------------------------------------------------------------ Function: alloca Allocates temporary stack space Syntax: #include void *alloca(size_t size); Remarks: alloca allocates bytes on the stack. The allocated space is automatically freed up when the calling function exits. Return value: o On success (if enough stack space is available), returns a pointer to the allocated stack area. o On error, returns null. Argument size is the number of bytes allocated on the stack. Because alloca modifies the stack pointer, do no place calls to alloca in an expression that is an argument to a function. NOTE: If the calling function does not contain any references to local variables in the stack, the stack won't be resotored correctly when the function exits and your program will crash. To ensure that the stack is restored correctly, use this code in your calling function: char *p; char dummy[1]; dummy[0] := 0;; ... p = alloca(nbytes); Because alloca is not defined in ANSI C, you should use malloc instead. See also: malloc ------------------------------------------------------------------
Welcome to Turbo C++ Version 3.0 -------------------------------- This README file contains important information about Turbo C++. For the latest information about Turbo C++ and its accompanying programs and manuals, read this file in its entirety. TABLE OF CONTENTS ----------------- 1. How to Get Help 2. Installation 3. Features 4. Important Information 5. Testing Your Expanded Memory 6. Corrections to the On-line Help 1. HOW TO GET HELP ------------------- If you have any problems, please read this file, the HELPME!.DOC and other files in your DOC subdirectory, and the Turbo C++ manuals first. If you still have a question and need assistance, help is available from the following sources: 1. Type GO BPROGB on the CompuServe bulletin board system for instant access to the Borland forums with their libraries of technical information and answers to common questions. If you are not a member of CompuServe, see the enclosed special offer, and write for full details on how to receive a free IntroPak containing a $15 credit toward your first month's on-line charges. 2. Check with your local software dealer or users' group. 3. Borland's TECHFAX service. Call (800) 822-4269 for a FAX catalog of entries. 4. If you have an urgent problem that cannot wait and you have sent in the license agreement that came with the package, you may call the Borland Technical Support Department at (408) 438-5300. Please have the following information ready before calling: a. Product name and serial number on your original distribution disk. Please have your serial number ready or we will be unable to process your call. b. Product version number. The version number for Turbo C++ can be displayed by pressing Alt-H/A. c. Computer brand, model, and the brands and model numbers of any additional hardware. d. Operating system and version number. (The version number can be determined by typing VER at the DOS prompt.) e. Contents of your AUTOEXEC.BAT file. f. Contents of your CONFIG.SYS file. 2. INSTALLATION ---------------- You MUST use the INSTALL program to install Turbo C++. The files on the distribution disks are all archived and have to be properly assembled. You cannot do this by hand! IMPORTANT! If you want to create backup copies of your disks, make sure that you put the backup on the same type of disk as the source. If you're backing up the 5 1/4 inch 1.2 Mb disk set, use only blank 5 1/4 inch 1.2 Mb disks for backup, etc. The installation will not work correctly if you do not use the same media type for the backup disks. To start the installation, change your current drive to the one that has the install program on it and type INSTALL. You will be given instructions in a box at the bottom of the screen for each prompt. For example, if you will be installing from drive A:, type: A: INSTALL - This INSTALL handles the installation of both the compiler and tools in one operation, and allows several new configuration options. - After installation, make sure you insert \TC\BIN - or whatever you selected as your BIN directory - into your DOS path so the executable files can be found. - Note: The list of files is contained in a separate file called FILELIST.DOC, which will appear in the target directory you specify during installation. - After your initial installation, you can run INSTALL again to add elements you omitted the first time. Just select the items you want to add in the INSTALL options screen. Because some things you may want to save could be overwritten, review the following items to make sure you don't lose important information: 1. Selecting CMD (the Command-line compiler) causes an overwrite of any existing turboc.cfg & tlink.cfg file with path information provided in that INSTALL session. Any switches other than -L (library path) and -I (include path) will not be preserved. 2. Selecting IDE will reset the include and library paths to those provided in that INSTALL session. 3. By selecting any one of the following, the help file paths and choices for THELP.CFG will reflect the current session's installation choices: a. CMD - command-line compiler b. IDE - integrated environment 4. Alterations to headers or startup files will be overwritten if any library models are selected. In general, any selection you make of something installed earlier will cause an overwrite of the earlier version without prompting. You should read the rest of this README file to get further information about this release before you do the installation. 3. FEATURES ------------ Turbo C++ 3.0 includes big speed and capacity gains. Here are some important features found in this version: - DPMI services for increased capacity - C++ 2.1 support, including the new nested class specifications, and support of C++ 3.0 templates. - Support for pre-compiled headers for substantial time savings during subsequent recompiles. - Color syntax highlighting - Unlimited Undo/Redo replacing previous 'restore line' capability - Added library functions for compatibility with other runtime libraries, and addition of support for long double parameters in math functions. (Please refer to On-line Help for details.) - New MAKE features. (Please see the MAKE chapter in the User's Guide for details.) - Added BGI (Borland Graphics Interface) fonts and support. (See "New BGI fonts" below.) - A resident DPMI kernel program, DPMIRES.EXE. (See "DPMI" below.) - THELP now allows you to switch between help files without unloading and reloading. (Please see UTIL.DOC for details.) NEW BGI FONTS ------------- Several new fonts have been added to the Borland Graphics Interface: Name Value Description ------------------------------------------- SCRIPT_FONT 5 Stroked script font SIMPLEX_FONT 6 Stroked simplex font TRIP_SCR_FONT 7 Stroked triplex script font COMPLEX_FONT 8 Stroked complex font EURO_FONT 9 Stroked European font BOLD_FONT 10 Stroked bold font The fonts in the BGI now support the full ASCII character set. DPMI ---- TC.EXE, TCC.EXE, and TLINK.EXE are now hosted under DPMI. These files support protected-mode compilation and replace the files of the same name in Turbo C++ Second Edition. Turbo C++ Second Edition should continue to be used in instances where real-mode compilation is desired. If you encounter a "machine not in database" message while attempting to run the compiler, run the DPMIINST program to add your machine configuration to the DPMI server database. This version includes a resident DPMI host program, DPMIRES.EXE, that allows you to preload the server before invoking TC, TCC, or any other DPMI-hosted executables. If you want to run such hosted EXEs in a Windows Standard Mode DOS window, you should run DPMIRES.EXE before loading Windows. To do this, enter the following commands at DOS: set DPMIMEM=MAXMEM 2000 dpmires win /s If you want to limit the amount of extended memory used by the DPMI-hosted executables, an environment variable called DPMIMEM can be set to do so. For instance, the command set DPMIMEM=MAXMEM 2000 reserves about 2 Mb of memory for DPMIRES. The number after MAXMEM can be adjusted, but cannot be lower than 1000. The hosted executables cannot spawn each other when SHARE is loaded. For instance, if you run MAKE on a file which in turn calls MAKE again, you will get a sharing violation. In this specific case, you can call the real mode version, MAKER, within the given makefile, and a sharing violation won't occur. 4. IMPORTANT INFORMATION ------------------------- - When using Brief with THELP, make sure to use Brief's -p switch to ensure that the thelp window will be visible. - We recommend that you use the following mouse drivers with this product: Microsoft Mouse version 7.04 or later; Logitech Mouse version 5.01 or later; Genius Mouse version 9.06 or later. - If you get a "floating point formats not linked" message at runtime, put the following somewhere in your source files: extern void _floatconvert(); #pragma extref _floatconvert This will force inclusion of floating point formats, which may not be linked to reduce executable size. COMPILER - The default extension for source files to the command-line compiler is .CPP; that is, if you enter TCC -c test the compiler will search for test.cpp, and give an error if a file of that name cannot be found. If you want to have the command-line compiler assume a .c extension and C language source, use the command-line option -P-c. For more information, see "The command-line compiler" in the User's Guide. - Note that the Generate COMDEFs choice under Options|Compiler|Advanced Code Generation and the -Fc command- line option are only supported in the C language. Linker errors will result if you attempt to use a communal variable in C++. - The macros min() and max() are not defined when stdlib.h is compiled as C++ (to allow their use in 3rd party libraries, etc.). - Note that SYMDEB creates .SYM files for use in debugging; Turbo C++ creates .SYM files for pre-compiled headers. They are not compatible and collisions should be avoided by setting the name of the pre-compiled header file (using - H=filename). - There is now full support of distance modifiers (near and far) used for class member pointers. Here are two sample declarations and their meanings: void (A::* far var) (); this is a far variable 'var' of type 'void (A::*)()'; void (far A::* var) (); this is a 'default distance' variable 'var' of type 'void (far A::*)()' - If you use C++ templates, and use a separate TLINK command line rather than letting TCC invoke TLINK, you should make sure that you turn on case-sensitive links with the /c switch. - Incorrect code will be generated if you have a statement of the type "A op B" where either A or B is an enum and the other operand is a long, and "op" is one of the following operators: += -= *= /= | ^ The same problem applies when the operands are a non-integer enum and an int. Cast the enum to long or int respectively to solve the problem. IDE - When debugging a mouse application the Options|Debugger|Display Swapping option should be set to "Always" for best results. - In the IDE, the mouse cursor is turned off during compilation for performance improvements. - To run or debug an overlaid application in the IDE when DOS SHARE is loaded, the .EXE file must first be marked as read-only. Otherwise, unload SHARE. - Pressing Control-Break twice while running or stepping a program from the IDE may cause unexpected results. In particular, avoid pressing Control-Break twice in response to any function requiring input (scanf, getch, etc.). To break out of a program during such interaction, press Control-Break and enter a valid input string. Control will be returned to the IDE. EXAMPLE PROGRAMS - When you are running any example programs that come with .PRJ files, if you didn't use the standard directories when you installed Turbo C++ you will have to change the .PRJ file to reflect your actual directory setup. Do this from inside Turbo C++ with Alt-O/D. LINKING C++ WITH C - Linking C++ modules with C modules requires the use of a linkage specification. Prototypes for C functions within C++ modules must be in one of the following forms: extern "C" declaration extern "C" { declarations } For example, if a C module contains these functions: char *SCopy(char*, char*); void ClearScreen(void) they must be declared in a C++ module in one of the following ways: extern "C" char *SCopy(char*, char*); extern "C" void ClearScreen(void); or extern "C" { char *SCopy(char*, char*); void ClearScreen(void); } Failure to do so will result in "Undefined symbol" errors during link. For further examples, see the standard header files. CLASS LIBRARY - Two versions of the class libraries are provided; one that includes debug information and one that does not. Small versions of each are provided, and project files are provided to build other models. Note that the non-debug versions are used by default. If you would like to use the debug version, copy it to the non-debug file. For instance, in the CLASSLIB\LIB directory, copy TCLASDBS.LIB to TCLASSS.LIB for the small model version. - In some places the User's Guide incorrectly refers to the online documentation for the Container Class Libraries as CONTAIN.DOC. The correct file name is CLASSLIB.DOC, located in the ..\DOC directory. 5. TESTING YOUR EXPANDED MEMORY: EMSTEST.COM --------------------------------------------- Included with Turbo C++ is a program to test your Expanded Memory hardware and software. If you have problems using Turbo C++ with your EMS, type EMSTEST at the DOS prompt and follow the instructions. 6. CORRECTIONS TO THE ON-LINE HELP ----------------------------------- The information for alloca is not available in on-line help. The correct help screen should read as follows: ------------------------------------------------------------------ Function: alloca Allocates temporary stack space Syntax: #include void *alloca(size_t size); Remarks: alloca allocates bytes on the stack. The allocated space is automatically freed up when the calling function exits. Return value: o On success (if enough stack space is available), returns a pointer to the allocated stack area. o On error, returns null. Argument size is the number of bytes allocated on the stack. Because alloca modifies the stack pointer, do no place calls to alloca in an expression that is an argument to a function. NOTE: If the calling function does not contain any references to local variables in the stack, the stack won't be resotored correctly when the function exits and your program will crash. To ensure that the stack is restored correctly, use this code in your calling function: char *p; char dummy[1]; dummy[0] := 0;; ... p = alloca(nbytes); Because alloca is not defined in ANSI C, you should use malloc instead. See also: malloc ------------------------------------------------------------------
二级减速器课程设计说明书,全英文书写 《Machine Parts Design》 Design Specification Topic Designation of Reducer College College of Mechanical and Electrical Engineering Major Mechanical Engineering Class 16机械工程3(国际化) No. of team Team 1 ID/Name 陈旭颖 16211452104 方 琢 16211452105 李成雍 16211452106 Instructor Zhang Yi Date submitted 2019.01.11 Contents Abstract 1 Chapter 1 Course Design Task Book 3 1.1 Purpose 3 1.2 Description of design project 3 1.3 Design Data 4 Chapter 2 Integral Design Scheme of Transmission Device 4 2.1 Transmission Scheme 4 2.2 Advantages and Disadvantages of this Scheme 4 Chapter 3 Selection of Motor 5 3.1 Motor Type Selection 5 3.2 Determination of the Efficiency of the Transmission 5 3.3 Selection of the motor capacity 5 3.4 Determination of the total transmission ratio and distribution transmission ratio of the transmission device 7 Chapter 4 Calculation of Dynamic Parameters 8 Chapter 5 Designation and calculation of high speed gear 11 5.1 Selection of gear type, accuracy grade, material and number of teeth 11 5.2 Design according to tooth surface contact fatigue strength 11 5.3 Determination of the sizes of transmission 15 5.4 Check the bending fatigue strength of tooth root 15 5.5 Calculations of other geometric dimensions of gear transmission 19 5.6 Summary of gear parameters and geometric dimensions 20 Chapter 6 Calculation of low-speed gear 21 6.1 Selection of gear type, accuracy grade, material and number of teeth 21 6.2 Designation according to tooth surface contact fatigue strength 22 6.3 Determination of the sizes of transmission 25 6.4 Check the bending fatigue strength of tooth root 26 6.5 Calculations of other geometric dimensions of gear transmission 30 6.6 Summary of gear parameters and geometric dimensions 30 Chapter 7 The designation of the shaft 32 7.1 Calculateion of High-speed shaft design 32 7.2 Calculation of jack shaft design 39 7.3 Calculation of low speed shaft 47 Chapter 8 Rolling bearing life check 53 8.1 Bearing check on high speed shaft 53 8.2 Bearing check on the jack shaft 55 8.3 Bearing check on the low speed shaft 57 Chapter 9 Key connection design calculation 58 9.1 Calculation check of coupling key connection 58 9.2 Calculation check of low speed pinion’s key connection 59 9.3 Calculation check of high speed main gear’s key connection 59 9.4 Calculation check of low speed main gear’s key connection 59 Chapter 10 Coupling selection 60 10.1 Coupling on the high speed shaft 60 10.2 Coupling on the low speed shaft 60 Chapter 11 Seal and lubricate the reducer 61 11.1 Selection of sealing 61 11.2 Gear lubrication 61 11.3 Bearing lubrication 62 Chapter 12 Reducer accessory 63 12.1 Oil level indicator 63 12.2 Ventilator 63 12.3 Drain plug 64 12.4 Peephole cover 65 12.5 Positioning pin 66 12.6 Cover screw 67 12.7 Lifting device 68 Chapter 13 Main structural dimensions of reducer housing 70 Chapter 14 Drawing of structure analysis of reduce 72 14.1 Drawing of assembly 72 14.2 Housing 73 14.3 Drawing of gears 74 14.4 Drawing of shafts 78 Chapter 15 Conclusion 81 15.1 Summary 81 15.2 Job description of team members 82 Reference 83 Attachment 84 Abstract Belt conveyor is a kind of friction driven to transport materials in a continuous way machinery. It Is mainly composed of irame conveyor belt, supporting roller, roller, tensioning device and belt conveyor motor device. It can put the material on a certain conveying line and form a conveying process of material from the initial feeding point to the final unloading point. It can not only carry out the transport of broken bulk materials, but also the transport of finished articles. In addition to the pure material transport, it can also cooperate with the requirements of the technological process in the production process of various industrial enterprises to form a rhythmic assembly line. Belt conveyor is widely used in metallurgy, coal, transportation, water and electricity, chemical and other departments, because it has a large amount of transport, simple structure, convenient maintenance, low cost, strong versatility and other advantages. Belt conveyor is also used in building materials, power, light industry, food, ports, ships and other departments. Main contents of this manual is for the design of belt conveyor drive system, the V belt transmission and twoestage cylindrical gear reducer, used in the design and calculation to the "machine design foundation", "mechanical drawing" "tolerance and interchangeability", “theoretical mechanics" courses, such as knowledge, and use AutoCAD software to carry on the drawing, so the comprehensive practice is a very important link, is also a comprehensive, standardized training in practice. Through this training, so that we have been in many aspects of training and training. It is mainly reflected in the following aspects. (1) we have cultivated the design idea of combining theory with practice, trained our ability to comprehensively apply the basic theory of mechanical design course and other related courses, analyze and solve practical engineering problems in combination with production practice, and consolidated, deepened and expanded the knowledge of relevant mechanical design. (2) through the standard mechanical parts. common mechanical transmission or simple mechanical design, so that we master the general mechanical design procedures and methods. establish a correct engineering desrgn Ideas. cultivate independence. comprehensive. Scientific engineering design ability and innovation ability. (3) in addition, it cultivates our ability to consult and use manuals, atlas and other relevant technical data, as well as the ability in calculation, drawing data processing and computer, aided design. (4) enhanced our understanding and application of the functions of Word and AutoCAD in office software. Keywords: reducer, transmission device, design, calculation, CAD Chapter 1 Course Design Task Book 1.1 Purpose According to the diagam of the belt conveyor system: (1) Plan and analysis of transmission device; (2) Selection of motor and calculation of kinematic and dynamic parameters in conveyor system; (3) Design of transmission parts (e.g. gear, worm or belt, etc.); (4) Design of shaft; (5) Design of bearing and its assemblies; (6) Selection and confirmation of key and coupling; (7) Design of lubrication; (8) Housing, framework and accessories; (9) Drawing of assembly and its components; (10) Design specification 1.2 Description of design project (a) running on two shifts per day in one-direction continuously; (b) stable loading; (c) starting with idling; (d) indoor setting with dust; (e) usage period: 10 years, minor overhaul period: 1 year, and overhaul period: 3 years; (f) power source is alternating three-phase voltage; (g) small-batch production in medium scale machinery plant; (h) allowed tolerance of conveyor speed is ± 5%. Working hours per day: 16 hours, working life: 10 years, working days per year: 300 days, equipped with three-phase AC power supply, voltage 380/220 V. 1.3 Design Data Working force of conveyor, F 2900N Speed of conveyor, v 1.5m/s Diameter, D 410mm Chapter 2 Integral Design Scheme of Transmission Device 2.1 Transmission Scheme Analysis of transmission scheme v-belt transmission is adopted . Considering the requirements of the project , I chose this scheme . Its transmission diagram is shown in figure 1-1. The transmission scheme has been given, and the reducer is a two-stage cylindrical gear reducer. 2.2 Advantages and Disadvantages of this Scheme The extemal outline size of this scheme is large, with good shock absorption capacity, low manufacturing, stability accuracy with low cost, and overload protection. But because the gear relative to the bearing of the two-stage cylindrical gear reducer is arranged asymmetrically, the load distribution along the tooth direction is uneven, and the shaft stiffness is required. Chapter 3 Selection of Motor 3.1 Motor Type Selection According to the use of the Y-series general purpose fully closed self-cooled three-phase asynchronous motor. 3.2 Determination of the Efficiency of the Transmission According to table 2-1, we got: The Efficiency of coupling:η1=0.99 The Efficiency of rolling bearing:η2=0.99 The Efficiency of closed cylindrical gears:η3=0.98 The Efficiency of Working Machine:ηw=0.97 Total efficiency from motor to machine: ηa=η1×η24×η32×ηw=0.877 3.3 Selection of the motor capacity The power required by the working machine Pw: Rated power required by motor Pd: Work speed of transmission belt wheels nw: According to the recommended reasonable transmission ratio range in table 2-2, the transmission ratio range of the expanded two-stage gear reducer ia=8 ~ 40, the transmission ratio range of v-belt transmission is ib=2~4, so the theoretical transmission ratio range is=16~160. The optional speed range of the motor : nd=is*nw=(16 ~ 160) 69.91=559--2796r/min. After comprehensive consideration of price, weight, transmission ratio and other factors, the selected three-phase asynchronous motor model : Y132M2-6 . Rated power Pen=5.5kW,Full load speed nm=960r/min,Synchronous speed nt=1000r/min。 Serial Number Motor Type Synchronous Speed/(r/min) Rated Power/kW Full Speed/(r/min) 1 Y160M2-8 750 5.5 720 2 Y132M2-6 1000 5.5 960 3 Y132S-4 1500 5.5 1440 4 Y132S1-2 3000 5.5 2900 Figure 3-1 main size parameters of the motor Height of Center Dimensionof overall Dimensionof base mounting Diameter of anchor bolt hole Size of Axis stretch Size of key H L×HD A×B K D×E F×G 132 515×315 216×178 12 38×80 10×33 3.4 Determination of the total transmission ratio and distribution transmission ratio of the transmission device (1)Calculation of total transmission ratio According to the selected fullload speed of the motor nm and the drive shaft speed of the motor nw,we can calculate the total transmission ratio of the transmission device ia: (2)Allocate transmission ratio High speed stage transmission ratio i1 Then the transmission ratio of low-speed stage i2 Total transmission ratio of reducer ib Chapter 4 Calculation of Dynamic Parameters (1)The speed of each shaft: High speed shaft : Jack shaft : Low speed shaft : The working machine shaft : (2)Input power of each shaft: High speed shaft : Jack shaft : Low speed shaft : The working machine shaft : Then the output power of each shaft: High speed shaft : Jack shaft : Low speed shaft : The working machine shaft : (3)Input torque of each shaft: Motor shaft : High speed shaft : Jack shaft : Low speed shaft : The working machine shaft : Then the torque of each shaft: High speed shaft : Jack shaft : Low speed shaft : The working machine shaft : The rotational speed, power and torque of each shaft are listed in the following table name of the shaft rotating speed n /(r/min) power P/kW torque T/(N•m) Motor shaft 960 4.96 49.34 High speed shaft 960 4.91 48.84 Jack shaft 222.74 4.76 204.09 Low speed shaft 69.82 4.62 631.92 The working machine shaft 69.82 4.35 594.99 Chapter 5 Designation and calculation of high speed gear 5.1 Selection of gear type, accuracy grade, material and number of teeth 1. According to the transmission scheme, helical cylindrical gear transmission is selected,Pressure angle α=20°,Primary spiral Angle β=12°。 2. Refer to table 10-6 for level 7 accuracy. 3. Material selection : According to table 10-1, Pinion chosen: 40Cr (quenched and tempered), hardness: 280HBS; Main gear: 45 (quenched and tempered), hardness: 240HBS. 4. Number of pinion teeth: z1=24,number of main gear teeth: z2=z1×i=24×4.31=103. 5.2 Design according to tooth surface contact fatigue strength 1. The diameter of the dividing circle of the pinion is calculated by formula (10-24),that is: (1) Determine the values of each parameter in the formula (1) Choose KHt=1.3 (2) Calculate the torque T transmitted by the pinion: (3) According to table 10-7, the tooth width coefficient: φd=1 (4) According to figure 10-20, regional coefficient: ZH=2.47 (5) According to table 10-5, the elastic influence coefficient of the material: ZE=189.8√MPa. (6)The contact fatigue strength Zε is calculated by formula (10-9). (7) The spiral Angle coefficient Zβ can be obtained from the formula. (8) Calculate the allowable contact fatigue stress[σH] According to figure 10-25d, the contact fatigue limit of pinion and large gear is respectively The stress cycle number is calculated from equation (10-15): Contact fatigue coefficients were obtained from FIG. 10-23 If the failure probability is 1% and the safety coefficient S=1,then: Take the smaller one of [σH]1 and [σH]2as the contact fatigue allowable stress of the gear pair, that is: (2) Calculate the diameter of the dividing circle of the pinion 2. Adjust the diameter of the dividing circle of the pinion (1) Data preparation before calculating actual load coefficient. (1) Circumferential velocity ν (2) Tooth width b (2) Calculate the actual load coefficient KH (1) According to table 10-2, KA=1 (2) According to v=1.827m/s and the accuracy of level 7, the dynamic load coefficient can be obtained from figure 10-8, Kv=1.035 (3) The circular force of a gear. In table 10-3, the load distribution coefficient between teeth was KH =1.4 When the accuracy of level 7 and the relative support of pinion are arranged asymmetrically by interpolation method, according to table 10-4, the distribution coefficient of load in tooth direction KHβ=1.417 Thus, the actual load coefficient KH is obtained (3) According to equation (10-12) and the actual load coefficient, the diameter of the dividing circle d1 can be obtained (4) Determine the modulus of 5.3 Determination of the sizes of transmission 1. Computing center distance a 2. The helix Angle is corrected according to the center distance after rounding β=12°19'58" 3. Calculate the dividing circle diameter d1 ,d2of small and big gear 4. Calculate the tooth width b Take B1=55mm, B2=50mm 5.4 Check the bending fatigue strength of tooth root The fatigue strength condition of tooth root bending: (1)T、mn and d1 are like the previous Tooth width: b=b2=50 Tooth shape coefficient YFa and stress correction coefficient YSa, the equivalent number of teeth: The equivalent number of teeth of pinion Zv1: Equivalent number of teeth of main gear Zv2: The tooth shape coefficient is obtained from FIG. 10-17 The stress correction coefficient is obtained from FIG. 10-18 (1) Choose load factor KFt=1.3 (2) From equation (10-18), the coincidence coefficient of bending fatigue strength Yε can be calculated Have a type: (3) From equation (10-19), obtain the spiral Angle coefficient of bending fatigue strength Yβ (2) Circumferential velocity (3) Aspect ratio b/h According to v=2.47m/s, level 7 accuracy, dynamic load coefficient can be found from figure 10-8, Kv=1.047 According to table 10-3 , load distribution coefficients between teeth KFα=1.4 According to table 10-4, KH =1.42 and b/h=50/4.5=11.111. According to figure 10-13, KF =1.079. Then the load coefficient is: According to FIG. 10-24c, the tooth root bending fatigue limit of pinion and big gear is respectively The bending fatigue coefficient KFN1 ,KFN2 was obtained from FIG. 10-22 The bending fatigue safety factor S=1.25, from equation (10-14) Check the bending fatigue strength of tooth root The bending fatigue strength of tooth root meets the requirement, and the ability of pinion to resist bending fatigue damage is greater than that of large gear. (4) The circular velocity of a gear Level 7 accuracy is appropriate. 5.5 Calculations of other geometric dimensions of gear transmission (1)Calculate the height of addendum tooth, dedendum tooth and total tooth (2)Calculate the addendum circle diameters of small and large gears (3)Calculate the diameter of dedendum circle of small and large gears 5.6 Summary of gear parameters and geometric dimensions Code name Calculated formula Pinion Main gear Modulus m 2 2 Spiral Angle β left-handed 12°19'58" right-handed 12°19'58" Coefficient of addendum height ha* 1.0 1.0 Tip clearance coefficient c* 0.25 0.25 Number of teeth z 24 103 Width of teeth B 55 50 Height of addendum teeth ha m×ha* 2 2 Height of dedendum teeth hf m×(ha*+c*) 2.5 2.5 Diameter of the dividing circle d 49.134 210.866 Addendum circle diameter da d+2×ha 53.134 214.866 Dedendum circle diameter df d-2×hf 44.134 205.866 Figure 5-1 structure diagram of high-speed main gear Chapter 6 Calculation of low-speed gear 6.1 Selection of gear type, accuracy grade, material and number of teeth 1. According to the transmission scheme, choose helical cylindrical gears,The pressure off for alpha = 20 °, primary spiral Angle beta = 12 °. 2. Refer to table 10-6 , choose level 7 accuracy. 3. Material selection According to table 10-1, choose pinion 40Cr (quenching and tempering), and the hardness was 280HBS; choose main gear 45 (quenching and tempering), and the hardness was 240HBS 4. Select the number of pinion teeth z1=25, then the number of large gear teethz2=z1×i=25×3.19=81. 6.2 Designation according to tooth surface contact fatigue strength 1. From formula (10-24), the diameter of the dividing circle of the pinion is calculated, i.e (1) Determine the values of each parameter in the formula (1) Choose KHt=1.3 (2) Calculate the torque transmitted by the pinion: (3) From table 10-7, the tooth width coefficient is φd=1 (4) From figure 10-20, Regional coefficient ZH=2.47 (5) From table 10-5, the elastic influence coefficient of the material ZE=189.8√MPa。 (6) From equation (10-9), the coincidence coefficient is used to calculate the contact fatigue strength Zε. (7) From the formula, the spiral Angle coefficient Zβ. (8) Calculate the allowable contact fatigue stress[σH] According to figure 10-25d, the contact fatigue limit of pinion and big gear is respectively From equation (10-15) , the number of stress cycles can be calculated : From figure10-23, check the contact fatigue coefficient If the failure probability is 1% and the safety coefficient S=1, then Take the smaller one of [σH]1 and [σH]2as the contact fatigue allowable stress of the gear pair, that is: (2) Calculate the diameter of the dividing circle of the pinion 2.Adjust the diameter of the dividing circle of the pinion (1) Data preparation before calculating actual load coefficient. (1) Circumferential velocity ν (2) Tooth width b (2) Calculate the actual load coefficient KH (1) According to table 10-2, KA=1 (2) According to v=0.666m/s and the accuracy of level 7, the dynamic load coefficient can be obtained from figure 10-8, Kv=1.013 (3) The circular force of a gear. In table 10-3, the load distribution coefficient between teeth was KH =1.2 When the accuracy of level 7 and the relative support of pinion are arranged asymmetrically by interpolation method, according to table 10-4, the distribution coefficient of load in tooth direction KHβ=1.421 Thus, the actual load coefficient KH is obtained (3) According to equation (10-12) and the actual load coefficient, the diameter of the dividing circle d1 can be obtained (4) Determine the modulus of 6.3 Determination of the sizes of transmission 1. Computing center distance a 2.The helix Angle is corrected according to the center distance after rounding β=12°43'9" 3. Calculate the dividing circle diameter d1 ,d2of small and big gear 4. Calculate the tooth width b Take B1=85mm B2=80mm 6.4 Check the bending fatigue strength of tooth root The fatigue strength condition of tooth root bending: (1)T、mn and d1 are like the previous Tooth width: b=b2=80 Tooth shape coefficient YFa and stress correction coefficient YSa, the equivalent number of teeth: Equivalent number of teeth of pinion Zv1: Equivalent number of teeth of main gear Zv2: The tooth shape coefficient is obtained from FIG. 10-17 The stress correction coefficient is obtained from FIG. 10-18 (1) Choose load factor KFt=1.3 (2) From equation (10-18), the coincidence coefficient of bending fatigue strength Yε can be calculated Have a type: (3) From equation (10-19), obtain the spiral Angle coefficient of bending fatigue strength Yβ (2) Circumferential velocity (3) Aspect ratio b/h According to v=0.9m/s, level 7 accuracy, dynamic load coefficient can be found from figure 10-8, Kv=1.017 According to table 10-3 , load distribution coefficients between teeth KFα=1.4 According to table 10-4, KHβ =1.427 and b/h=80/6.75=11.852. According to figure 10-13, KF =1.08. Then the load coefficient is: According to FIG. 10-24c, the tooth root bending fatigue limit of pinion and big gear is respectively The bending fatigue coefficient KFN1 ,KFN2 was obtained from FIG. 10-22 The bending fatigue safety factor S=1.25, from equation (10-14) Check the bending fatigue strength of tooth root The bending fatigue strength of tooth root meets the requirement, and the ability of pinion to resist bending fatigue damage is greater than that of large gear. (4) The circular velocity of a gear Level 7 accuracy is appropriate. 6.5 Calculations of other geometric dimensions of gear transmission (1)Calculate the height of addendum tooth, dedendum tooth and total tooth (2)Calculate the addendum circle diameters of small and large gears (3)Calculate the diameter of dedendum circle of small and large gears 6.6 Summary of gear parameters and geometric dimensions Code name Calculated formula Pinion Main gear Modulus m 3 3 Spiral Angle β left-handed 12°43'9" right-handed 12°43'9" Coefficient of addendum height ha* 1.0 1.0 Tip clearance coefficient c* 0.25 0.25 Number of teeth z 25 81 Width of teeth B 85 80 Height of addendum teeth ha m×ha* 3 3 Height of dedendum teeth hf m×(ha*+c*) 3.75 3.75 Diameter of the dividing circle d 76.887 249.113 Addendum circle diameter da d+2×ha 82.887 255.113 Dedendum circle diameter df d-2×hf 69.387 241.613 Figure 6-1 Low speed large gear structure drawing Chapter 7 The designation of the shaft 7.1 Calculateion of High-speed shaft design 1. Select the material on the shaft and determine the allowable stress Because the reducer is a general machine, there is no special requirement, so 40Cr (quenched and tempered) is selected, the hardness is 280HBS, check the table15-1,take σb=735MPa, σ-1b=60MPa 2. The minimum diameter of the shaft estimated according to the initial torsion strength Check table 15-3, take A0=112,so Shaft ends have 1 keyway, therefore, the axle diameter should be increased by 5% According to the table, the diameter of the standard axle hole is 22mm, so d=22 Figure 7-1 Schematic diagram of high-speed shaft (1) The minimum diameter of the input shaft is obviously d12, where the coupling is mounted. In order to adapt the selected shaft diameter d12 to the coupling aperture, the type of coupling should be selected. The calculated torque of the coupling Tca = KA×T, according to the table, thinking about the stability, we choose KA = 1.3, then: According to the condition that the torque Tca of the coupling should be less than the nominal torque of the coupling, refer to standard GB t4323-2002 or design manual, choose LX3 type coupling. The aperture of the semi-coupling is 22mm, the hub hole length of the semi-coupling and the shaft is 52mm. Choose ordinary flat keys,A type keys, b×h = 6×6mm(GB T 1096-2003), bond length L=40mm。 (2) Initial selection of rolling bearing. Since the bearing is subject to both radial and axial forces, angular contact bearing is selected. Referring to the work requirements and according to d23 = 27mm, select 7206AC angular contact bearing from bearing product catalog, its size: d×D×B = 30×62×16mm, so d34 = d78 = 30 mm. The positioning shaft shoulder height of 7206AC type bearing is found in the manual, h = 3 mm,then choose d45 = d67 = 36 mm. (3)Because the diameter of the gear is small, in order to ensure the strength of the gear wheel body, the gear and the shaft should be made into one and become the gear shaft. So l56 = 55 mm, d56 = 53.134 mm. (4) Thickness of bearing end covere=10, thickness of the gasketΔt=2. According to the bearing end cover for easy assembly and disassembly, ensure that the outer end face of the bearing end cover has a certain distance from the end face of the coupling, K=24; Screw C1=22mm, C2=20mm, thickness of box seat wall δ=8mm, then: (5) Take small spacing distance of enclosure wall Δ1 = 10 mm, the distance between high speed main gear and low speed pinion Δ3 = 15 mm distance. Considering about the housing casting error, when determining the position of rolling bearing, a distance Δ from inner wall of box should be taken, take Δ = 10 mm, the width of low speed pinion b3=85mm, then: At this point, the diameter and length of each section of the shaft have been preliminarily determined. Shaft section 1 2 3 4 5 6 7 Diameter / mm 22 27 30 36 53.134 36 30 Length/ mm 52 65 28 105.5 55 8 28 3. Stress analysis of the shaft The circumferential force on a high speed pinion Ft1 (d1 is the diameter of the indexing circle of the high-speed pinion) Radial force on a high speed pinion Fr1 Axial force on a high speed pinion Fa1 According to 7206AC angular contact manual, pressure center a=18.7mm Distance between the center point of the first shaft and the bearing pressure center l1: Distance from bearing pressure center to gear fulcrum l2: Distance between gear midpoint and bearing pressure center l3: (1) Calculate the supporting reaction of the shaft Horizontal support reaction: Vertical support reaction: (2) Calculate the bending moment of the shaft, and draw the bending moment diagram The horizontal bending moment at section C: The vertical bending moment at section C: Bending moment diagram of horizontal plane (fig.b) and vertical plane (fig.c). The resultant bending moment at section C: (3) Make composite bending moment diagram (figure d) Make torque diagram (figure e) Figure 7-2 High - speed shaft force and bending moment diagram 4. Check the strength of the shaft Because the bending moment on the left side of C is large and the action has torque, the left side of C is the dangerous section. The bending section coefficient W: The torsion cross section coefficient WT: The maximum bending stress: The shear stress: Check and calculate according to the strength of bending and torsion. For the shaft of one-way drive, torque is processed according to pulsating cycle. Therefore, the reduced coefficient is adopted α=0.6, then the equivalent stress is (10) Check the table, get 40Cr(tempering and tempering) treatment, and the limit of tensile strength σB=735MPa; Then the allowable bending stress of the axis [σ-1b]=60MPa, σca<[σ-1b], so the strength is good. 7.2 Calculation of jack shaft design 1. Select the material on the shaft, and determine the allowable stress Because the reducer is a general machine, there is no special requirements, so choose 45 (quenched and tempered), the hardness: 240HBS. Referring table 15-1, take σb=640MPa, σ-1b=60MPa 2. According to the initial torsion strength, the minimum diameter of the shaft estimated Refer to table 15-3, take A0=112, then: Since the minimum diameter of the shaft section is all rolling bearings, the standard diameter d=35mm is selected. Figure 7-3 Diagram of intermediate shaft (1) Initial selection of rolling bearing. The minimum diameters of the intermediate shaft are d12 and d56 for mounting the rolling bearing. Because the bearing is subject to both radial and axial forces, angular contact bearing is chosen. Referring to the requirement of working and according to dmin = 31.08 mm, from the bearing catalogue, selsct angular contact bearing 7207AC, its size: d×D×B = 35×72×17mm, so d12 = d56 = 35 mm. (2) At the installation of the big gear, take the diameter of the shaft section d45 = 38mm; Positioning by oil baffle ring is taken between the right end of the gear and the right bearing. It is known that the width of the hub of the high-speed large gear wheel b2 = 50mm, in order to press gears reliably, this section should be slightly shorter than the width of the hub, then take l45 = 48 mm. Shaft shoulder positioning is adopted in the left end of the gear, the height of shaft shoulder h = (2~3)R. Refer to the table with trunnion d45 = 38 mm, take h = 5 mm, then the diameter of Collar point d34 = 48 mm. Collar width b≥1.4h, take l34 = 15 mm. (3) Left end rolling bearing adopts oil baffle ring for axial positioning. (4) Considering about material and machining economy, low speed pinion and shaft should be designed and manufactured separately. It is known that the hub width of the low-speed pinion is b3= 85mm, in order to make the end face of oil retaining ring press the gear reliably, this section should be slightly shorter than the width of the hub, so take l23 = 83 mm,d23=38mm。 (5) Take the distance between the low-speed pinion and the inner wall of the boxΔ1 =10 mm, the distance between the high speed big gear and the inner wall of the box Δ2 =12.5 mm, the distance between high speed main gear and low speed pinionΔ3=15mm. Consider housing casting error, when determining the position of rolling bearing, should be from a distance Δ casing wall, take Δ = 10 mm, then: At this point, the diameter and length of each section of the shaft have been preliminarily determined. Shaft section 1 2 3 4 5 Diameter/ mm 35 38 48 38 35 Length/ mm 39 83 15 48 41.5 3. Force analysis of the shaft The circumferential force on a high speed pinion Ft2 (d2 is the diameter of the indexing circle of the high-speed pinion) Radial force on a high speed pinion Fr2 Axial force on a high speed pinion Fa2 Circumferential force on the low-speed pinion Ft3 (d3 is the dividing circle diameter of the low-speed pinion) Radial force on a low speed pinion The axial force on a low speed pinion According to 7207AC angular contact manual, pressure center a=21mm Distance from bearing pressure center to middle point of low-speed pinion: Distance from the midpoint of the low-speed pinion to that of the high-speed large gear: Distance from the middle point of the high-speed large gear to the bearing pressure center: (1) Calculate the reaction force of the shaft Horizontal support reaction Vertical support reaction (2) Calculate the bending moment of the shaft and draw the bending moment diagram The horizontal bending moment at section B The horizontal bending moment at section C The vertical bending moment at section C The vertical bending moment at section B Draw the bending moment diagram of horizontal plane (fig.b) and vertical plane (fig.c) The resultant bending moment at section B The synthetic bending moment of section C: Make composite bending moment diagram (figure d) Make torque diagram (figure e) Figure 7-4 force and bending moment of jack shaft 4. Check the strength of the shaft Because the bending moment on the left side of B is large and the action has torque, the left side of B is the dangerous section. Its bending section coefficient: Its torsion cross section coefficient: The maximum bending stress: Its shear stress: Check and calculate according to the strength of bending and torsion. For the shaft of one-way drive, torque is processed according to pulsating cycle. Therefore, the reduced coefficient is adopted α=0.6, then the equivalent stress is Check the table, get 40Cr(tempering and tempering) treatment, and the limit of tensile strength σB=640MPa; Then the allowable bending stress of the axis [σ-1b]=60MPa, σca<[σ-1b], so the strength is good. 7.3 Calculation of low speed shaft 1. Select the material on the shaft, and determine the allowable stress Because the reducer is a general machine, there is no special requirements, so choose 45 (quenched and tempered), the hardness: 240HBS. Referring table 15-1, take σb=640MPa, σ-1b=60MPa 2. According to the initial torsion strength, the minimum diameter of the shaft estimated Refer to table 15-3, take A0=112, then: Shaft end has 1 keyway, so increase shaft diameter by 7% According to the table, the diameter of the standard axle hole is 50mm, so d=50 Figure 7-5 Schematic diagram of low-speed shaft (1) The minimum diameter of the output shaft is obviously the diameter d1 of the shaft where the coupling is mounted. In order to make the selected shaft diameter d1 match the coupling aperture, it is necessary to select the type of coupling.The calculated torque of the coupling Tca = KA×T, refer to the table, consider about stability, then take KA = 1.3,thus: According to the condition that the torque Tca of the coupling should be less than the nominal torque of the coupling, check the standard GB t4323-2002 or the design manual, choose LX4 type coupling. The aperture of the semi-coupling is 50mm, the hub hole length of fitness of the semi-coupling and the shaft is 112mm. Choose ordinary flat bond, A type bond, b×h = 14×9mm(GB T 1096-2003), length of bond L=100mm. (2) Initial selection of rolling bearing. Because the bearing is subject to both radial and axial forces, angular contact bearing is chosen. According to work requirements and d23 = 55mm, angular contact bearing 7212AC is selected from the bearing product catalog, its size: d×D×B = 60×110×22mm, so d34 = d78 = 60 mm. Positioning of bearing oil retaining ring. According to the manual, the positioning shaft shoulder height of type 7212AC bearing is h = 4.5mm, so d45 = 69mm (3) Take the diameter of the shaft section where the gear is mounted d67 = 63 mm;The width of the low-speed large gear hub is known as b4 = 80 mm,in order to make the end face of the oil retaining ring press the gear reliably, this shaft segment should be slightly shorter than the width of the hub, so l67 = 78mm. The left end of the gear is fixed by the shaft shoulder. The height of shaft shoulder h = (2~3)R,The diameter of the shaft d67 = 63 mm, so take h = 10 mm, then the diameter at the collar d56 = 83 mm, take l56=10mm. (4) Thickness of bearing end cover e=10, the thickness of the gasket Δt=2. According to the ease of mounting and dismounting of the bearing end cover, ensure that the outer end face of the bearing end cover has a certain distance from the end face of the coupling K=24, screw C1=22mm, C2=20mm, box seat wall thickness δ=8mm, then: (5) Assume the distance between low level main gear and inner box wall Δ 2 = 12.5 mm, the distance between high speed main gear and low speed pinion Δ 3 = 15 mm distance. Consider housing casting error, when determining the position of rolling bearing, should be from a distance Δ casing wall, assume Δ = 10 mm, then: At this point, the diameter and length of each section of the shaft have been preliminarily determined. Shaft section 1 2 3 4 5 6 7 Diameter 50 55 60 69 83 63 60 Length 112 59 44.5 57.5 10 78 46.5 3. Force analysis of the shaft Circumferential force on the low-speed big gear (d4 is the dividing circle diameter of the low-speed big gear) The radial force on a large low speed gear The axial force exerted on a large low-speed gear Refer to the manual with 7212AC angular contaction, know pressure center a=30.8mm (1)Calculate the supporting reaction of the shaft Horizontal support reaction Vertical support reaction (2) Calculate the bending moment of the shaft and draw the bending moment diagram The horizontal bending moment at section C The vertical bending moment at section C Draw the bending moment diagram of horizontal plane (fig.b) and vertical plane (fig.c) The resultant bending moment at section C (3) Make composite bending moment diagram (figure d) Make torque diagram (figure e) Figure 7-6 Diagram of force and bending moment of low speed shaft 4. Check the strength of the shaft Because the bending moment on the left side of C is large and the action has torque, the left side of C is the dangerous section Its bending section coefficient: Its torsion cross section coefficient: The maximum bending stress: Its shear stress: Check and calculate according to the strength of bending and torsion. For the shaft of one-way drive, torque is processed according to pulsating cycle. So the reduced coefficient =0.6, then the equivalent stress: Refer to the the table, get 45(tempering) treatment, tensile strength limitσB=640MPa,then the allowable bending stress of the axis[σ-1b]=60MPa, σca<[σ-1b], so the strength is good. Chapter 8 Rolling bearing life check 8.1 Bearing check on high speed shaft Bearing code d(mm) D(mm) B(mm) Cr(kN) C0r(kN) 7206AC 30 62 16 22 14.2 Adopt 7206AC angular contact ball bearing, inner diameter d=30mm, outer diameter D=62mm, width B=16mm, Basic dynamic load rating Cr=22kN,Rated static load C0r=14.2kN. Life expectancy is Lh=48000h. According to the horizontal and vertical bearing reaction calculated previously, we can calculate the resultant bearing reaction: Axial force Fae=435N According to the calculations, bearing 1 is "pressed", while bearing 2 is “relaxing”. Refer to the table, X1=0.41,Y1=0.87,X2=1,Y2=0 Refer to the table, ft=1,fp=1 Then, take the bigger one into Bearing life is sufficient. 8.2 Bearing check on the jack shaft Bearing code d(mm) D(mm) B(mm) Cr(kN) C0r(kN) 7207AC 35 72 17 29 19.2 Adopt 7207AC angular contact ball bearing, inner diameter d=35mm, outer diameter D=72mm, width B=17mm, Basic dynamic load ratingCr=29kN, Rated static load C0r=19.2kN Life expectancy is Lh=48000h. According to the horizontal and vertical bearing reaction calculated previously, we can calculate the resultant bearing reaction: Axial force Fae=775N According to the calculations, bearing 1 is "pressed", while bearing 2 is “relaxing”. Refer to the table, X1=0.41,Y1=0.87,X2=1,Y2=0 Refer to the table, ft=1,fp=1 Then, take the bigger one into Bearing life is sufficient. 8.3 Bearing check on the low speed shaft Bearring code d(mm) D(mm) B(mm) Cr(kN) C0r(kN) 7212AC 60 110 22 58.2 46.2 Adopt 7212AC angular contact ball bearing, inner diameter d=60mm, outer diameter D=110mm, width B=22mm, Basic dynamic load rating Cr=58.2kN,Rated static load C0r=46.2kN Life expectancy is Lh=48000h。 According to the horizontal and vertical bearing reaction calculated previously, we can calculate the resultant bearing reaction: Axial force Fae=1145N According to the calculations, bearing 1 is "pressed", while bearing 2 is “relaxing”. Refer to the table, X1=0.41,Y1=0.87,X2=1,Y2=0 Refer to the table, ft=1,fp=1 Then, take the bigger one into Bearing life is sufficient. Chapter 9 Key connection design calculation 9.1 Calculation check of coupling key connection The chosen type of key is A-type: 6×6(GB/T 1096-2003) Working length of key: l=L-b=40-6=34mm Contact height of the hub keyway: k=h/2=3mm According to the material of the coupling which is 45 and the stability of loading, we can get [σp]=120MPa, then it’s compression strength is It meets the strength requirement. 9.2 Calculation check of low speed pinion’s key connection The chosen type of key is A-type: 10×8(GB/T 1096-2003) Working length of key: l=L-b=70-10=60mm Contact height of the hub keyway: k=h/2=4mm According to the material of the low speed pinion which is 40Cr and the stability of loading, we can get [σp]=120MPa, then it’s compression strength is It meets the strength requirement. 9.3 Calculation check of high speed main gear’s key connection The chosen type of key is A-type: 10×8(GB/T 1096-2003) Working length of key: l=L-b=36-10=26mm Contact height of the hub keyway: k=h/2=4mm According to the material of the high speed main gear which is 45 and the stability of loading, we can get [σp]=120MPa, then it’s compression strength is It meets the strength requirement. 9.4 Calculation check of low speed main gear’s key connection The chosen type of key is A-type: 18×11(GB/T 1096-2003) Working length of key: l=L-b=63-18=45mm Contact height of the hub keyway: k=h/2=5.5mm According to the material of the low speed main gear which is 45 and the stability of loading, we can get [σp]=120MPa, then it’s compression strength is It meets the strength requirement. Chapter 10 Coupling selection 10.1 Coupling on the high speed shaft (1)Calculate the load on the coupling Refer to the table, the load coefficient of the coupling is KA=1.3 Then calculate the torque is Tc=KA×T=1.3×48.84=63.5N•m (2)Select the type of coupling Primary coupling model is LX3 elastic pin coupling (GB/ t4323-2002). Refer to the table, Nominal torque Tn=1250N•m, Allowable speed[n]=4700r/min, thus: Tc=63.5N•mSelect the type of coupling Primary coupling model is LX3 elastic pin coupling (GB/ t4323-2002). Refer to the table, Nominal torque Tn=2500N•m, Allowable speed[n]=3870r/min, thus: Tc=821.5N•mSelection of sealing In order to prevent the leakage of lubricant inside the box and the entry of external impurities into the box to affect the work of the box, between the parts that make up the box, such like the box cover and the box seat, the output of the overhanging shaft, the input shaft and the bearing cover, different types of sealing devices are required. For the joint surface without relative motion, commonly used sealant, oil resistant rubber gasket, etc. For the sealing of rotating parts such as overhanging shaft, different seals and structures should be considered according to their different motion speed and sealing requirements. In this design, because the relative speed of sealing interface is small, contact seal is adopted. The velocity between the input shaft and the bearing cover is V <3m/s, the velocity between the output shaft and the bearing cover is also V 1.2δ 12mm Distance between gear face and inner box wall △2 >δ 12.5mm Case cover and seat rib thickness m1、m m1≈0.85×δ1、m≈0.85×δ 8mm、8mm Outer diameter of high speed bearing end cap D1 D+(5~5.5)d3;D--bearing outer diameter 102mm Outer diameter of end cover of jack bearing D2 D+(5~5.5)d3;D--bearing outer diameter 112mm Outer diameter of low speed bearing end cap D3 D+(5~5.5)d3;D--bearing outer diameter 150mm Chapter 14 Drawing of structure analysis of reduce 14.1 Drawing of assembly 14.2 Housing 14.3 Drawing of gears High speed main gear Low speed pinion 14.4 Drawing of shafts High speed shaft Jack speed shaft Low speed shaft Chapter 15 Conclusion 15.1 Summary After hard work, I finally finished the mechanical design course. In the process of this operation, I encountered many difficulties. The repeated calculation and the design scheme modification exposed my lack of knowledge and experience in this aspect in the early stage, and I learned the lesson of blind calculation. As for drawing assembly drawing and part drawing, due to sufficient preliminary calculation, the whole process took less than three days. During this period, I also received a lot of help from my classmates and teachers. Here I would like to express my most sincere thanks to them. Although the time of this assignment is long and the process is tortuous, for me, the biggest gain is the method and ability. The ability to analyze and solve problems. In the whole process, I found that what students like us most lack is experience, no perceptual knowledge, empty theoretical knowledge, and some things may be out of touch with the reality. In general, I think doing this type of homework is of great help to us. It requires us to systematically connect the relevant knowledge we have learned, expose our shortcomings and make improvements. Sometimes a person's power is limited, the wisdom of all people, I believe our work will be more perfect! Due to the limited time, there are many shortcomings in this design, such as the huge box structure and large weight. The gear calculation is not accurate enough and other defects, I believe, through this practice, I can avoid a lot of unnecessary work in the future design, have the ability to design a more compact structure, transmission more stable and accurate equipment. 15.2 Job description of team members Team leader: 陈旭颖 Finish the designation and calculation of transmission device, motor, dynamic parameters, rolling bearings, keys and couplings. Draw the CAD of assembly drawing and reducer housing drawing. Write the design specification. Team members: 方琢 Finish the designation and calculation of high speed gear, jack gear and low speed gear. Draw the CAD of high speed gear, jack gear and low speed gear. 李成雍 Finish the designation and calculation of high speed shaft, intermediate shaft and low speed shaft. Draw the CAD of high speed shaft, intermediate shaft and low speed shaft. Reference [1] Kunwoo Lee, Principles of CAD/CAM/CAE Systems, Pearson, Jan., 1999. [2] Chris McMahon and Jimmie Browne, CAD/CAM Principles, Practices and Manufacturing Management (2/e), Prentice Hall, July, 1999. [3] Andrew D. Dimarogonas, Machine Design - A CAD Approach, John Wiley & Sons, Dec. 2000. [4] E. Paul Degarmo, J. T. Black and Ronald A. Kohser, Materials and Processes in Manufacturing (11th edition), Wiley, Dec. 2011. [5] 李育锡. 机械设计课程设计(第⼆版). 北京:⾼等教育出版社. in Chinese [6] 陈秀宁. 机械设计课程设计(第四版). 杭州:浙江⼤学出版社. 2010. in Chinese [7] 吴宗泽. 机械设计课程设计. 北京:⾼等教育出版社. 2007. in Chinese [8] 闻邦椿. 机械设计⼿册 1-6 卷(第五版). 北京:机械⼯业出版社. 2011. in Chinese Attachment 1.The drawing of assembly; 2.The drawing of reducer housing; 3.The drawing of pinion; 4.The drawing of main gear; 5.The drawing of low speed shaft; 6.The drawing of jack shaft; 7.The drawing of high speed shaft;

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