Clutch mating surface grinding device

Abstract

This invention provides a grinding device for the mating surfaces of a clutch, belonging to the technical field of parts grinding equipment. The grinding device includes a base plate, a clamping grinding assembly, a crank rocker mechanism, a drive system, and a control system. This invention grinds the mating surfaces of the clutch shaft and the spiral sleeve using the clamping grinding assembly and crank rocker mechanism, replacing traditional manual grinding. This reduces the grinding time from 4-6 hours to two 1-hour grinding sessions, achieving the same grinding effect as qualified products and improving grinding efficiency. This device requires only one person to install and operate the parts, reducing manual labor. The drive and control systems enable standardization, ensuring consistent high-quality grinding of parts. All parts meet process requirements after grinding, with stable quality. The grinding time can be adjusted based on the grinding effect, allowing for targeted adaptation to individual parts, balancing batch stability and individual adaptability.

Description

Technical Field

[0001] This invention belongs to the technical field of parts grinding equipment, and specifically relates to a grinding device for the mating surfaces of a clutch. Background Technology

[0002] This series of products is a core component of an important platform. Its dedicated clutch is a critical component in the transmission and control system of this series of products, enabling precise control and quantitative supply of materials during operation. Its transmission stability and operational accuracy directly determine the reliability and precision of the entire equipment. The clutch shaft and the helical sleeve, forming a paired transmission pair, are the core structure for achieving uniform load transmission and precise motion control. To avoid localized stress concentration and abnormal wear during high-speed operation, the process explicitly requires that the contact rate of the mating surfaces of these two components be no less than 50%. The grinding process is a crucial step in ensuring this precision.

[0003] Currently, the grinding of the helical mating surfaces of the clutch shaft and the helical sleeve relies entirely on manual grinding. After applying grinding paste to the mating surfaces, operators manually rotate and push the workpiece repeatedly to achieve grinding, requiring multiple disassembly and reassembly inspections and repeated grinding. However, this method is inefficient, labor-intensive, and critical parameters such as grinding pressure and workpiece coaxiality depend entirely on manual experience, resulting in extremely poor grinding quality stability. It is prone to problems such as substandard contact rate of the mating surfaces and uneven wear, ultimately leading to wear and jamming of the clutch at high speeds, causing abnormal transmission control and even irreversible damage to precision parts, posing significant operational risks. Summary of the Invention

[0004] The purpose of this invention is to solve the problems of low processing efficiency, high labor intensity and low grinding quality caused by manual grinding of the mating surfaces of existing clutches. The invention provides a grinding fixture that can replace manual grinding, simplify manual operation and improve efficiency and grinding quality. The fixture mechanism is designed according to the actual working process of the clutch shaft and the spiral sleeve to simulate the motion process in order to achieve effective grinding of the mating surfaces.

[0005] To achieve the above objectives, the technical solution provided by this invention is:

[0006] A clutch mating surface grinding device is provided, wherein the clutch shaft in the clutch is located in a helical sleeve, and the outer helical surface of the clutch shaft mates with the inner helical surface of the helical sleeve to form a mating surface. The device includes a base plate, a clamping grinding assembly, a crank rocker mechanism, and a drive system. The base plate supports the clamping grinding assembly, the crank rocker mechanism, and the drive system. The clamping grinding assembly includes a first bracket, a second bracket, a clamping element, and a drive shaft. The first and second brackets are mounted to the base plate. The first bracket supports the clutch shaft and restricts its circumferential rotation, while the second bracket rotatably supports the drive shaft. The transmission shaft and the clutch shaft are coaxially arranged. A clamping member is fixedly connected to one end of the transmission shaft and located between the first bracket and the second bracket. The clamping member is used to clamp the spiral sleeve and make the clutch shaft and the spiral sleeve coaxial and able to make contact. The crank rocker mechanism is mounted on the base plate and is used to drive the transmission shaft to reciprocate. It includes a crank, a rocker, and a connecting rod that is rotatably connected to the crank and the rocker respectively. The rocker is fixedly connected to the other end of the transmission shaft. The drive system is mounted on the base plate and fixedly connected to the crank. It is used to drive the crank rocker mechanism to move. The control system is electrically connected to the drive system and is used to control the drive system.

[0007] Furthermore, the rocker swing range in the crank-rocker mechanism is based on the axial length of the outer helical surface of the clutch shaft, the axial thickness of the inner helical surface of the helical sleeve, and the lead settings of the outer and inner helical surfaces.

[0008] Furthermore, the rocker arm swing range in the crank-rocker mechanism is 38.57°~77.14°.

[0009] Furthermore, the crank angle difference between the two extreme positions of the joystick is close to 180°.

[0010] Furthermore, the drive system includes a driver and a stepper motor. The stepper motor is connected to the crank, and the driver is electrically connected to the stepper motor. The speed and torque of the stepper motor are adjusted according to the tightness of the clutch mating surfaces.

[0011] Furthermore, the control system includes a controller, intermediate relays, time-delay relays, and a power module. The controller is electrically connected to the driver and is used to receive grinding start commands and control the start and stop of the driver. The intermediate relay is electrically connected to the controller and is used to maintain the self-locking circuit after startup. The time-delay relay is electrically connected to the intermediate relay and the controller and is used to set the grinding time. After the timer expires, it outputs a stop signal to the controller, disconnects the self-locking state of the intermediate relay, and realizes the automatic reset of the control system. The power module is electrically connected to the controller, time-delay relay, and intermediate relay respectively and is used to provide power to the control system.

[0012] Furthermore, the outer wall of the end of the clutch shaft away from the outer helical surface has a spline; the central hole of the first bracket for passage has a groove that mates with the spline, so that the clutch shaft can move axially but cannot rotate.

[0013] Furthermore, a long flat key is installed between the first bracket and the second bracket to ensure the alignment between the first bracket and the second bracket.

[0014] Furthermore, the control system also includes a buzzer; the time-delay relays include a first time-delay relay and a second time-delay relay; the first time-delay relay is electrically connected to the intermediate relay, the controller, the buzzer, and the second time-delay relay respectively, and is used to set the grinding time, and when the grinding time is reached, the controller stops working, and at the same time triggers the buzzer to work and puts the second time-delay relay into working state; the second time-delay relay is electrically connected to the buzzer and the intermediate relay, and is used to trigger the second time-delay relay to time after the driver is started; the second time-delay relay is electrically connected to the buzzer and the intermediate relay, and is used to set the buzzer prompt time, and when the buzzer time is reached, the intermediate relay is released from the self-locking state, thereby causing the first time-delay relay and the buzzer to stop working, completing the reset of the control system.

[0015] The advantages of this invention are:

[0016] 1. This invention relates to a clutch mating surface grinding device. Through a set clamping grinding assembly and crank rocker mechanism, it grinds the mating surfaces of the clutch shaft and spiral sleeve, replacing traditional manual grinding. This reduces the grinding time from 4-6 hours to two 1-hour grinding sessions, achieving the same grinding effect as qualified products and improving grinding efficiency. This device requires only one person to complete the installation and operation of the parts, reducing manual labor. By setting up a drive system and control system, standardization can be achieved, ensuring that the grinding quality of the parts maintains the same high requirements. This ensures that all parts meet the process requirements after grinding, resulting in stable quality. Furthermore, the grinding time can be adjusted according to the grinding effect, allowing for targeted adaptation of individual parts, balancing batch stability and individual adaptability.

[0017] 2. This invention discloses a clutch mating surface grinding device. Utilizing the interaction between a spiral sleeve and the clutch shaft, a crank-rocker mechanism drives the spiral sleeve to reciprocate, thereby causing the clutch shaft to move reciprocally and achieving grinding of the mating surfaces. This device replicates the actual motion process, significantly improving the grinding effect. Ideally, it can achieve perfect uniform contact and fitting precision on the mating surfaces, ensuring high stability and reliability during clutch operation. Attached Figure Description

[0018] The features and advantages of the invention will become more readily apparent from the following description with reference to the accompanying drawings, which are not drawn to scale and some features are enlarged or reduced to show details of specific parts.

[0019] Figure 1 This is a schematic diagram of the structure of a clutch mating surface grinding device according to the present invention;

[0020] Figure 2 This is a schematic diagram showing the positional relationship between the clamping and grinding assembly, the clutch shaft, and the spiral sleeve of the present invention;

[0021] Figure 3 This is a schematic diagram of one extreme position of the rocker arm in the crank-rocker mechanism of the present invention;

[0022] Figure 4 This is a schematic diagram of another extreme position of the rocker arm in the crank-rocker mechanism of the present invention;

[0023] Figure 5 This is the electrical schematic diagram of the control system of the present invention;

[0024] Figure 6 This is a schematic diagram of the wiring of the controller output port of the present invention;

[0025] Figure 7 This is a timing diagram of the control signals for the software program of this invention.

[0026] In the diagram: 1-base plate; 2-grinding assembly; 21-first bracket; 22-second bracket; 23-chuck; 24-drive shaft; 25-long flat key; 3-crank rocker mechanism; 31-crank; 32-rocker; 33-connecting rod; 4-drive system; 41-motor; 5-clutch shaft; 6-screw sleeve. Detailed Implementation

[0027] The present invention will now be described in detail with reference to the accompanying drawings and exemplary embodiments thereof. It should be noted that the following detailed description of the present invention is for illustrative purposes only and is not intended to limit the scope of the invention.

[0028] The clutch in this embodiment is a key component in the transmission and control system of a certain series of products. During operation, it enables precise control and quantitative supply of materials. The clutch shaft 5 is housed within the spiral sleeve 6, and the outer spiral surface of the clutch shaft 5 mates with the inner spiral surface of the spiral sleeve 6 to form a contact surface. In actual use, the spiral sleeve 6 remains axially fixed. The relative rotation between the spiral sleeve 6 and the clutch shaft 5 controls the forward or backward movement of the clutch shaft 5 along its axis, thereby disengaging or engaging the transmission. Therefore, to ensure the clutch shaft 5 can smoothly complete its forward and backward movement, the contact spiral surfaces of the clutch shaft 5 and the spiral sleeve 6 must fit well. Grinding the surfaces ensures that both spiral surfaces are smooth and their shapes are well-matched.

[0029] Based on actual working conditions, the clutch shaft 5 is required to reciprocate within the spiral sleeve 6, such as... Figure 1 As shown, this embodiment provides a clutch mating surface grinding device, including a base plate 1, a clamping grinding assembly 2, a crank rocker mechanism 3, a drive system 4, and a control system.

[0030] like Figure 1 As shown, the base plate 1 is used to support and clamp the grinding assembly 2, the crank-rocker mechanism 3, and the drive system. In this embodiment, the base plate 1 is an L-shaped structure with a horizontal plate and a vertical plate. In other embodiments, it can also be a rectangular or other component capable of supporting and clamping the grinding assembly 2, the crank-rocker mechanism 3, and the drive system.

[0031] like Figure 1 , 2 As shown, the clamping and grinding assembly 2 includes a first bracket 21, a second bracket 22, a clamping member, and a drive shaft 24. The first bracket 21 and the second bracket 22 are respectively installed at both ends of the horizontal plate, with the second bracket 22 near the bend of the base plate 1. The first bracket 21 supports the clutch shaft 5 and restricts its circumferential rotation. The second bracket 22 supports the drive shaft 24 in a rotatable manner, and the drive shaft 24 is coaxial with the clutch shaft 5. The clamping member is fixedly connected to the right end of the drive shaft 24 and located between the first bracket 21 and the second bracket 22. The clamping member clamps the spiral sleeve 6 and makes the clutch shaft 5 and the spiral sleeve 6 coaxial and capable of contact engagement. By setting the first bracket 21, the second bracket 22, the clamping member, and the drive shaft 24, the clutch shaft 5 and the spiral sleeve 6 are on the same axis, allowing the clutch shaft 5 to reciprocate axially within the spiral sleeve 6. In this embodiment, two second brackets 22 are provided to support both ends of the drive shaft 24.

[0032] In this embodiment, the clamping element is a four-jaw chuck 23, which can extend into the groove in the outer wall of the spiral sleeve 6 for clamping; in another possible embodiment, the clamping element can also be a three-jaw chuck 23, which clamps by extending its jaws into the groove. In addition, the clamping element is not limited to the form of chuck 23, and other devices that can extend into the groove and apply radial clamping force can also be used, such as elastic chucks or specialized clamps.

[0033] like Figure 1 , 2 As shown, the crank-rocker mechanism 3 is mounted on the vertical plate and is used to drive the transmission shaft 24 to reciprocate. It includes a crank 31, a rocker 32, and a connecting rod 33 that is rotatably connected to the crank 31 and the rocker 32 respectively. The rocker 32 is fixedly connected to the left end of the transmission shaft 24. The drive system 4 is mounted on the vertical plate and fixedly connected to the crank 31. It is used to drive the crank-rocker mechanism 3 to move. The control system is electrically connected to the drive system 4 and is used to control the drive system 4.

[0034] The control system controls the drive system 4 to move, driving the crank-rocker mechanism 3 to move. The crank 31 rotates at a constant speed, and the crank 31 drives the rocker arm 32 to reciprocate through the connecting rod 33, causing the spiral sleeve 6 and the rocker arm 32 to reciprocate together. The clutch shaft 5 is installed in the first bracket 21, and the outer spiral surface of the clutch shaft 5 mates with the inner spiral surface of the spiral sleeve 6. This causes the clutch shaft 5 to reciprocate linearly when the spiral sleeve 6 reciprocates, thereby ensuring that the outer spiral surfaces of the spiral sleeve 6 and the clutch shaft 5 are fully engaged, completing the grinding action.

[0035] This invention discloses a clutch mating surface grinding device. Through a clamping grinding assembly 2 and a crank rocker mechanism 3, the device grinds the mating surfaces of the clutch shaft 5 and the spiral sleeve 6, replacing traditional manual grinding. This reduces the grinding time from 4-6 hours to two 1-hour grinding sessions, achieving the same grinding effect as qualified products and improving grinding efficiency. The device requires only one person to install and operate the parts, reducing manual labor. Standardization is achieved through a drive system 4 and a control system, ensuring consistent high-quality grinding of parts. This guarantees that all parts meet process requirements after grinding, resulting in stable quality. Furthermore, the grinding time can be adjusted based on the grinding effect, allowing for targeted adaptation of individual parts, balancing batch stability with individual adaptability.

[0036] The outer wall of the end of the clutch shaft 5 away from the outer helical surface has a spline, which is used to restrict rotation. The upper end of the first bracket 21 has a groove in the center hole through which the clutch shaft 5 passes, which mates with the spline, allowing the clutch shaft 5 to move axially but preventing rotation. A long flat key 25 is installed between the first bracket 21 and the second bracket 22, and the long flat key 25 is inserted into the mounting groove at the center of the bottom of the first bracket 21 and the second bracket 22 to ensure alignment between the two brackets.

[0037] The drive system 4 includes a driver and a stepper motor 41. The driver is electrically connected to the stepper motor 41 and adjusts the speed and torque of the stepper motor 41 according to the tightness of the clutch mating surfaces. The output shaft of the stepper motor 41 is connected to one end of the crank 31. The stepper motor 41 is mounted on the base plate 1 via a motor bracket.

[0038] In this embodiment, the drive system 4 uses a DM860H driver and an 86-stepper motor 41. The DM860H uses a latest 32-bit processor as its core, offering various current and microstepping settings to meet the needs of most applications. Due to its built-in microstepping technology, it can achieve high microstepping even at low microstepping levels, ensuring smooth operation at low, medium, and high speeds with extremely low noise. The driver features motor 41 parameter learning and automatic control parameter tuning, as well as adaptive parameter adjustments during operation. It can automatically generate optimal operating parameters for different motors 41, maximizing the performance of the motor 41.

[0039] The 86 stepper motor 41 uses imported silicon steel bearings and is manufactured using German technology. Its surface is coated with rotor rubber to prevent silicon steel oxidation and reduce surface burrs after grinding. Motor 41 offers greater torque, more stable output, lower noise, and a longer lifespan. The motor 41 coil uses 100% pure copper enameled wire with advanced winding technology, resulting in uniform copper wire distribution. This leads to lower temperature rise and prevents deformation and noise issues during long-term load operation.

[0040] The DM860H driver uses an eight-bit DIP switch to set the microstepping accuracy, dynamic current, and half-current / full-current settings. Through adjustments, the grinding equipment set the DM860H driver's microstepping accuracy to 20000 pulses / rev, and the full-current setting to a peak current of 7.2A and a continuous current of 6A. The rated torque of the 86 stepper motor 41 is 8 N·m.

[0041] In this embodiment, the swing range of the rocker arm 32 in the crank rocker mechanism 3 is based on the axial length of the outer helical surface of the clutch shaft 5, the axial thickness of the inner helical surface of the helical sleeve 6, and the lead settings of the outer and inner helical surfaces.

[0042] Specifically, both the outer and inner helical surfaces should be ground along their entire length. Let the axial thickness of the helical sleeve 6 be *a*, and the axial length of the helical surface of the clutch shaft 5 be *b*. On one hand, the forward and backward movement distance of the clutch shaft 5 should not be less than *b* to ensure that the inner helical surface of the helical sleeve 6 can contact the outer helical surface of the clutch shaft 5 along its entire axial thickness. Since the lead of the helical surfaces of the clutch shaft 5 and the helical sleeve 6 is *l*, to ensure that the forward and backward movement of the clutch shaft 5 is not less than *b*, the minimum angle θ of the reciprocating swing range of the rocker arm 32 is... min=b / l×360°. On the other hand, the helical surface of the clutch shaft 5 should always be partially within the helical sleeve 6, and not completely separated, to ensure that the positioning and grinding processes can continue. Therefore, the forward and backward movement distance of the clutch shaft 5 should not be greater than a. Therefore, the maximum angle θ of the reciprocating swing range of the rocker arm 32 is... max =a / l×360°.

[0043] In this embodiment, the axial thickness a of the spiral sleeve 6 is 24mm, the axial length b of the helical surface of the clutch shaft 5 is 12mm, and the lead l of the helical surfaces of the clutch shaft 5 and the spiral sleeve 6 is 112mm. Therefore, the reciprocating swing range of the rocker arm 32 should not be less than 12 / 112×360°=38.57°, and the reciprocating swing range of the rocker arm 32 should not be greater than 24 / 112×360°=77.14°. Thus, the swing range of the rocker arm 32 in the crank-rocker mechanism 3 is 38.57°~77.14°.

[0044] Since the helical sleeve 6 performs reciprocating grinding, the forward and reverse movements should be uniform. Therefore, the angle difference between the crank 31 corresponding to the two extreme positions of the rocker arm 32 should be as close as possible to 180°, so that the forward and reverse movements of the rocker arm 32 are basically symmetrical when the crank 31 rotates at a constant speed.

[0045] Based on the above analysis, the reciprocating motion range of the rocker arm 32 is set to 54° (the clutch shaft 5 moves back and forth by 16.8 mm). The radius of the crank 31 is set to R1, the radius of the rocker arm 32 is set to R2, the horizontal distance between the axes of the motor 41 output shaft and the clutch shaft 5 (i.e., the baseline) is set to L, and the length of the connecting rod 33 is set to C.

[0046] In this example, there are no direct restrictions on the lengths of crank 31, rocker arm 32, connecting rod 33, and drive shaft 24. Some lengths can be determined according to requirements, and then the lengths of other rods can be calculated. (In actual design, the dimensions of some components will be limited by actual design conditions. First, meet the limited dimensions, and then design the dimensions of other rods based on these conditions.)

[0047] like Figure 3 As shown, considering the actual size limitations of the mechanism, the baseline length is set to L=500mm. To facilitate assembly and confirm the position, one extreme position of the rocker arm 32 is set to 90° upward.

[0048] set up Then, the other extreme position of the joystick 32 is when the joystick 32 rotates 54° and makes an angle of 36° with the baseline L, such as Figure 4 As shown, then there is .

[0049] If the length of joystick 32 is set to C=100mm, then... ,

[0050] The calculated radius of crank 31 is R1 = 43.35 mm, and the length of connecting rod 33 is C = 466.55 mm.

[0051] Verification using the above-mentioned length diagram revealed that the angle difference between the crank 31 corresponding to the two extreme positions of the rocker arm 32 is 176.67°, close to 180°, which meets the design requirements. Therefore, in this embodiment, the crank 31 radius is R1=43.35mm, the rocker arm 32 radius is R2=100mm, the center distance (baseline) between the motor 41 output shaft and the transmission shaft 24 is L=500mm, and the connecting rod 33 length is C=466.55mm.

[0052] like Figure 5 As shown, the control system includes a controller K1, an intermediate relay KM1, a time delay relay, and a power module U1. The controller K1 is electrically connected to the driver and is used to receive the grinding start command and control the start and stop of the driver. The intermediate relay KM1 is electrically connected to the controller K1 and is used to maintain the self-locking circuit after startup. The time delay relay is electrically connected to the intermediate relay KM1 and the controller K1 and is used to set the grinding time. After the timer ends, it outputs a stop signal to the controller K1, cuts off the self-locking state of the intermediate relay KM1, and realizes the automatic reset of the control system. The power module U1 is electrically connected to the controller K1, the time delay relay, and the intermediate relay KM1 respectively and is used to provide power to the control system.

[0053] The controller K1 uses software to control the output voltage of the driver, thereby adjusting the speed of the motor 41. The controller K1 is a system circuit board based on the ATmega328p microcontroller. It can be used to develop electronic products that need to operate independently and have interactive effects, as well as interactive products that connect to a computer and work in collaboration with software.

[0054] The main performance characteristics of the controller K1 are as follows: (1) 12 digital input / output ports D2-D13; (2) 8 analog input ports A0-A7; (3) 1 pair of TTL level serial transceiver ports RX / TX; (4) 6 PWM ports D3, D5, D6, D9, D10 and D11; (5) Supports USB download and power supply; (6) External 3.3V-12V DC power supply; (7) Supports ISP download.

[0055] The main function of controller K1 is to output pulse control signals, motor 41 running direction signals, and enable signals to the driver. The output frequency of the pulse signals can be set via buttons on the controller K1 panel, further controlling the output voltage of the driver to control the speed of motor 41. System wiring is as follows: Figure 6 As shown.

[0056] PUL pulse control signal (core control command for stepper motor 41 driver): Employs a pulse rising edge-effective response mode, with a high-level input range of 4–5V and a low-level input range of 0–0.5V. For reliable pulse signal response, the pulse width should be greater than 1.2μs. When using +12V PUL- or +24V, no series resistor is required; it can be directly adaptively controlled by the driver.

[0057] When the input mode is pulse + direction, DIR acts as the direction signal: the high / low level signal determines the rotation direction of motor 41. To ensure reliable commutation of motor 41, the direction signal should be established at least 5μs before the pulse signal. The initial running direction of motor 41 is related to the wiring of motor 41. Interchanging any phase winding (e.g., swapping A+ and A-) can change the initial running direction of motor 41. DIR- is 4-5V when high and 0-0.5V when low. If +12V or +24V is used, no series resistor is required, and the driver is adaptive.

[0058] When the input mode is dual pulse, DIR acts as a reverse pulse signal: its characteristics are the same as those of pulse signals PUL+ and PUL-; when the input mode is encoder follow, DIR acts as a B-phase pulse signal: its characteristics are the same as those of pulse signals PUL+ and PUL-.

[0059] ERC Enable Signal (Enable state of controller K1 driver): This input signal is used to enable or disable. When ENA+ is connected to +5V and ENA- is connected to a low level (or the internal optocoupler is turned on), the driver will cut off the current to each phase of motor 41, putting motor 41 in a free state. At this time, the step pulse will not be responded to. When this function is not needed, the enable signal terminal can be left floating.

[0060] The software is developed using the Arduino IDE environment and programmed in C. The main function of the program is to... Figure 7 The timing shown causes controller K1 to output the corresponding signal.

[0061] The control system also includes a buzzer LS1; the time delay relays include a first time delay relay KT1 and a second time delay relay KT2; the first time delay relay KT1 is electrically connected to the intermediate relay KM1, the controller K1, the buzzer LS1, and the second time delay relay KT2, respectively, and is used to set the grinding time. When the grinding time is reached, the controller K1 stops working, and the buzzer LS1 is triggered to work, and the second time delay relay KT2 enters the working state; the second time delay relay KT2 is electrically connected to the buzzer LS1 and the intermediate relay KM1, and is used to trigger the second time delay relay KT2 to keep time after the driver is started; the second time delay relay KT2 is electrically connected to the buzzer LS1 and the intermediate relay KM1, and is used to set the buzzer prompt time. When the buzzer time is reached, the intermediate relay KM1 is released from its self-locking state, thereby causing the first time delay relay KT1 and the buzzer LS1 to stop working, and completing the reset of the control system.

[0062] The control system enables controllable grinding time, and the control circuit automatically cuts off power and sounds a buzzer to alert the operator after grinding is completed. When the grinding device malfunctions, the power module U1 can be forcibly cut off by disconnecting the self-locking switch S2 to avoid damage to the clutch shaft 5 and the spiral sleeve 6, thus ensuring personnel safety.

[0063] like Figure 5 As shown, the input terminal of the self-reset switch S1 is connected to DC24V+, and the output terminal of the self-reset switch S1 is connected to the positive pin 14 of the intermediate relay KM1 coil and the positive pin 4 of the second time delay relay KT2 coil. The negative pins 13 and 2 of the intermediate relay KM1 and the second time delay relay KT2 coil are both connected to DC24V- to form a complete power supply circuit. At the same time, the normally open self-locking contact of the controller K1 is also connected in parallel to the output terminal of the self-reset switch S1 to realize the circuit self-locking function. After the intermediate relay KM1 coil is energized, its two sets of parallel normally open contacts close. Connect DC24V+ to the positive pin 7 of the controller K1 coil. The negative pin 2 of the controller K1 coil is connected to DC24V- through the normally closed contact of the second time delay relay KT2 to form a circuit. The normally closed contact of the controller K1 is connected in series in the negative circuit of the first time delay relay KT1 coil. The positive pin 3 of the first time delay relay KT1 coil is directly connected to DC24V+. One end of the normally open contact of the first time delay relay KT1 is connected to DC24V+, and the other end is connected to the positive terminal of the buzzer LS1. The negative terminal of the buzzer LS1 is directly connected to DC24V-.

[0064] The drive system 4 provides adjustable grinding speed while maintaining a certain torque, allowing for adjustments to both torque and grinding speed based on the tightness of the mating surfaces of the parts. The output torque of motor 41 is adjusted and matched; excessive torque can cause over-grinding or even damage to the parts, and prolonged high power output from motor 41 can lead to overheating or overcurrent protection of the driver, reducing the tooling's lifespan. The driver controls the output power via DIP switches, thereby adjusting the torque of motor 41. In case of overvoltage or overcurrent, the driver cuts off the enable signal for protection. This achieves a good grinding effect within a short grinding time, and the driver can be set to reverse the mechanism according to the movement requirements of the parts, increasing the feasibility for grinding other types of parts. Finally, the driver drives a crank-rocker mechanism 3 via motor 41, converting the rotation of the motor 41's output shaft into reciprocating rotation within a fixed angle (54°), achieving automatic grinding.

[0065] Grinding device assembly process:

[0066] like Figure 2 As shown, firstly, the first and second supports are installed onto the base plate 1 using bolts and spring washers; then, the motor 41 is fixed onto the motor 41 bracket, and the internal spline of the crank 31 is installed onto the output shaft of the motor 41 and tightened with screws; subsequently, the drive shaft 24 is installed onto the second bracket 22, and the rocker arm 32 is fixed onto the drive shaft 24 and tightened with screws; then, the connecting rod 33, crank 31, and rocker arm 32 are connected together with pin bolts, the positions of each support are adjusted, and a long flat key 25 is inserted between the first and second supports to ensure the alignment between each support, and finally the bolts are tightened.

[0067] The process of installing grinding parts on the grinding device:

[0068] like Figure 2 As shown, connecting rod 33 and crank 31 are adjusted as follows: Figure 2 When a straight line is shown, the clutch shaft 5 is installed on the first bracket 21 to ensure the starting position of grinding. The position of the connecting rod 33 can be slightly adjusted. The chuck 23 is used to hold the outer wall of the spiral sleeve 6. The relative position of the outer spiral surface of the clutch shaft 5 and the spiral sleeve 6 can be slightly adjusted so that the four jaws of the chuck 23 are in the groove on the outer wall of the spiral sleeve 6. At the same time, the right end face of the outer spiral surface of the clutch shaft 5 is aligned with the right end face of the inner spiral surface of the spiral sleeve 6, and the left end face of the outer spiral surface of the clutch shaft 5 is aligned with the left end face of the inner spiral surface of the spiral sleeve 6.

[0069] Control system operation process:

[0070] The self-reset switch S1 inputs a low-level signal V to the controller K1 pin, starting the controller's operating program and controlling the drive system 4 to drive the crank-rocker mechanism 3 for grinding. The intermediate relay KM1, while powered on, self-locks and inputs DC24V to the first delay relay KT1 for grinding timing. The grinding time is set via the first delay relay KT1. When the grinding time reaches the preset time, the normally open contact of the delay relay closes, and the controller K1 pin receives another low-level signal V, stopping the grinding. The buzzer LS1 is powered on and sounds an alarm. Simultaneously, DC24V is input to the second delay relay KT2 for buzzing timing. The buzzing time is set via the second delay relay KT2. When the buzzing time reaches the preset time, the normally closed contact of the second delay relay KT2 opens, the intermediate relay KM1 is de-energized, and consequently, the first delay relay KT1 is de-energized, stopping the buzzing alarm.

[0071] Finally, it should be noted that the features mentioned and / or shown in the above description of exemplary embodiments of the present invention can be combined in the same or similar manner with one or more other embodiments, combined with features in other embodiments, or substituted for corresponding features in other embodiments. These combined or substituted technical solutions should also be considered to be included within the scope of protection of the present invention.

Claims

1. A clutch mating surface grinding device, wherein the clutch shaft (5) in the clutch is located in a spiral sleeve (6), and the outer spiral surface of the clutch shaft (5) and the inner spiral surface of the spiral sleeve (6) mate to form a mating surface, characterized in that, It includes a base plate (1), a clamping and grinding assembly (2), a crank rocker mechanism (3), a drive system (4), and a control system; The base plate (1) is used to support the clamping and grinding assembly (2), the crank rocker mechanism (3), and the drive system; The clamping and grinding assembly (2) includes a first bracket (21), a second bracket (22), a clamping member, and a drive shaft (24). The first bracket (21) and the second bracket (22) are mounted on the base plate (1). The first bracket (21) is used to support the clutch shaft (5) and restrict the circumferential rotation of the clutch shaft (5). The second bracket (22) is used to support the drive shaft (24) in a rotatable manner, and the drive shaft (24) and the clutch shaft (5) are coaxially arranged. The clamping member is fixedly connected to one end of the drive shaft (24) and located between the first bracket (21) and the second bracket (22). The clamping member is used to clamp the spiral sleeve (6) and make the clutch shaft (5) and the spiral sleeve (6) coaxial and able to make contact. The crank-rocker mechanism (3) is mounted on the base plate (1) and is used to drive the transmission shaft (24) to reciprocate. It includes a crank (31), a rocker (32) and a connecting rod (33) that is rotatably connected to the crank (31) and the rocker (32) respectively. The rocker (32) is fixedly connected to the other end of the transmission shaft (24). The drive system (4) is mounted on the base plate (1) and fixedly connected to the crank (31) for driving the crank rocker mechanism (3) to move; The control system is electrically connected to the drive system (4) and is used to control the drive system (4).

2. The clutch mating surface grinding device according to claim 1, characterized in that, The swing range of the rocker arm (32) in the crank rocker mechanism (3) is based on the axial length of the outer helical surface of the clutch shaft (5), the axial thickness of the inner helical surface of the helical sleeve (6), and the lead settings of the outer and inner helical surfaces.

3. The clutch mating surface grinding device according to claim 1, characterized in that, The rocker arm (32) in the crank-rocker mechanism (3) swings within a range of 38.57° to 77.14°.

4. The clutch mating surface grinding device according to claim 3, characterized in that, The crank (31) angle difference between the two extreme positions of the rocker (32) is close to 180°.

5. The clutch mating surface grinding device according to claim 1, characterized in that, The drive system (4) includes a driver and a stepper motor (41). The stepper motor (41) is connected to the crank (31). The driver is electrically connected to the stepper motor (41) and adjusts the speed and torque of the stepper motor (41) according to the tightness of the clutch mating surfaces.

6. The clutch mating surface grinding device according to claim 5, characterized in that, The control system includes a controller, an intermediate relay, a time-delay relay, and a power module. The controller is electrically connected to the driver and is used to receive the grinding start command and control the start and stop of the driver. The intermediate relay is electrically connected to the controller and is used to maintain the self-locking circuit after startup. The time-delay relay is electrically connected to the intermediate relay and the controller and is used to set the grinding time. After the timer expires, it outputs a stop signal to the controller, disconnects the self-locking state of the intermediate relay, and realizes the automatic reset of the control system. The power module is electrically connected to the controller, the time-delay relay, and the intermediate relay respectively and is used to provide power to the control system.

7. The clutch mating surface grinding device according to claim 1, characterized in that, The outer wall of the end of the clutch shaft (5) away from the outer helical surface has a spline; The first bracket (21) has a groove in the center hole for passing through the clutch shaft (5) that engages with the spline so that the clutch shaft (5) can move along its axial direction but cannot rotate.

8. The clutch mating surface grinding device according to claim 1, characterized in that, A long flat key (25) is installed between the first bracket (21) and the second bracket (22) to ensure the alignment between the first bracket (21) and the second bracket (22).

9. The clutch mating surface grinding device according to claim 6, characterized in that, The control system also includes a buzzer; The time-delay relay includes a first time-delay relay and a second time-delay relay. The first time-delay relay is electrically connected to an intermediate relay, a controller, a buzzer, and the second time-delay relay, respectively. It is used to set the grinding time and, when the grinding time is reached, to stop the controller from working, simultaneously triggering the buzzer and putting the second time-delay relay into working state. The second time-delay relay is electrically connected to the buzzer and the intermediate relay and is used to trigger the second time-delay relay to keep time after the driver is started. The second time-delay relay is also electrically connected to the buzzer and the intermediate relay and is used to set the buzzer prompt time. When the buzzer time is reached, it releases the self-locking state of the intermediate relay, thereby stopping the first time-delay relay and the buzzer from working, thus completing the reset of the control system.

Images