Plunger type static pressure clutch

Abstract

The invention provides a plunger type static pressure clutch which comprises a static pressure clutch part which comprises a driving end, a transmission end and a driven end with an inner curved surface. A plunger hole and an oil discharge narrow slit are formed in the cavity wall of the driving end, and a pressure oil duct is formed in the oil supply shaft in the cavity; the transmission end comprises an oil inlet disc, and a one-way valve is arranged on the oil inlet disc. The plunger is embedded in the plunger hole, and a pin roller is embedded in the plunger in a rolling mode. The inner cavity is divided into a first chamber and a second chamber by the oil trapping piston; the oil discharge narrow slit is arranged corresponding to the first chamber, and the second chamber is communicated with the pressure oil duct; the oil trapping piston is connected to the cavity through the piston spring. According to the clutch, the torque transmission requirement is met by using the clutch with lighter weight, meanwhile, the combination process of the clutch can be actively controlled, the combination pressure is smoothly increased, and violent impact in the separation and reunion process is avoided.

Description

Technical Field

[0001] This application relates to the field of mechanical transmission technology, and in particular to a plunger-type hydrostatic clutch. Background Technology

[0002] In power transmission systems, clutches are frequently used to control the output and interruption of power. Clutches are widely used in automobiles, ships, engineering and agricultural machinery, and other fields. A clutch has an input end and an output end. When the clutch is engaged, the input and output ends are connected, and power from the input end is output from the output end. When the clutch is disengaged, the input and output ends are disconnected, and power cannot be transmitted. When one end is connected to a fixed component such as a housing, it functions as a brake.

[0003] Common clutches include dry or wet friction plate clutches, and slant-type or roller-type overrunning clutches. Dry and wet friction plate clutches are the most widely used in the transmission field. A friction plate clutch contains one or more friction pairs composed of steel plates and friction discs. The steel plates and friction discs are connected to the input and output ends respectively. Under the push of the actuating parts, the steel plates and friction discs can move axially to achieve engagement and disengagement. When the steel plates and friction discs are separated, the input and output shafts are disconnected, and power cannot be transmitted. When the steel plates and friction discs are engaged, friction is generated under the action of engagement pressure, thereby enabling the transmission of torque. Slant-type or roller-type overrunning clutches typically consist of an outer ring, an inner ring, and rolling elements. The outer and inner rings are connected to the input and output shafts respectively. Their core function is to allow power to be transmitted in one direction and automatically disengage in the opposite direction, achieving "overrunning" freewheeling.

[0004] Friction clutches typically use friction pairs made of paper, copper, or carbon fiber. The torque they can transmit increases with the engagement pressure, but once the engagement pressure reaches a certain value, the transmitted torque reaches its limit. Further increasing the pressure to increase the transmitted torque will result in friction material shedding and ablation. The allowable pressure is generally between 1-4 MPa. Therefore, when transmitting larger torques, it is necessary to increase the number of friction pairs and the diameter of the friction plates, which often results in a large size and weight, making them unsuitable for transmission applications requiring lightweight design. Overrunning clutches, on the other hand, use high-strength alloy steel for their friction contact pairs. They rely on friction to self-lock and transmit torque and can operate at very high engagement pressures. They have high power density and a simple structure, but engagement is instantaneous with a huge impact. Furthermore, they generally produce a passive engagement and disengagement action, and cannot be actively controlled according to demand. They can only be used in applications requiring unidirectional torque transmission. Summary of the Invention

[0005] To address the aforementioned problems, the present invention aims to provide a plunger-type hydrostatic clutch that enables the use of a lighter clutch to meet torque transmission requirements, while also allowing active control of the clutch engagement process, smoothly increasing engagement pressure, and avoiding severe impacts during engagement.

[0006] To achieve this objective, the present invention provides a plunger-type hydrostatic clutch, the technical solution of which is as follows: A plunger-type hydrostatic clutch includes a hydrostatic clutch portion, the hydrostatic clutch portion including a driving end, a driven end and a transmission end, the transmission end being disposed on the driving end and in movable contact with the driven end, so as to separate or engage the driving end and the driven end. The active end includes a cavity and an oil supply shaft. The cavity includes an inner cavity through which the oil supply shaft passes and a cavity wall forming the inner cavity. The cavity wall has interconnected plunger holes and oil discharge slits. The oil supply shaft has a pressure oil passage for injecting pressure oil. The passive end has a curved surface. The transmission end includes: A one-way valve is provided on the cavity and located at the position where the pressure oil passage and the plunger hole are connected, for controlling the flow of pressure oil between the pressure oil passage and the plunger hole; A plunger is movably fitted into the plunger hole, and a groove is provided on the side of the plunger facing the curved surface, in which a roller is rolled and fitted. An oil trapping piston is sleeved between the oil supply shaft and the cavity wall, and movably divides the inner cavity into a first chamber and a second chamber; the oil discharge slit is provided corresponding to the first chamber, and the second chamber is connected to the pressure oil passage, which is used to drive the oil trapping piston to move axially towards the first chamber under the action of pressure oil, thereby blocking the oil discharge slit; A piston spring is disposed on the cavity and abuts against the oil trapping piston, used to drive the oil trapping piston to move axially toward the second chamber when the pressure oil injection is stopped, thereby connecting the oil discharge slit and the first chamber.

[0007] As one of the preferred embodiments, the transmission end includes an oil inlet plate, which is sleeved between the oil supply shaft and the cavity wall, and the one-way valve is disposed on the oil inlet plate.

[0008] As one of the preferred embodiments, the inner side of the plunger is provided with a narrow venting slit that connects the plunger hole and the groove.

[0009] As one preferred embodiment, the transmission end further includes a compression spring, which is fixed to the cavity wall and abuts against the plunger.

[0010] As one preferred embodiment, the cavity includes an input shaft and a cylinder, the input shaft and the cylinder being fixedly connected; the passive end includes a fixed outer shell and an output shaft, the outer shell being sleeved on the outer periphery of the cavity, and the inner side of the outer shell being composed of multiple evenly distributed curved surfaces forming a closed curved surface.

[0011] As one preferred embodiment, multiple plunger holes and multiple oil drain slits are provided, the multiple plunger holes are spaced apart along the circumference of the cylinder body and are correspondingly connected to the multiple oil drain slits; and each plunger hole is correspondingly provided with each plunger hole, each plunger is correspondingly provided with each roller, and the multiple rollers are in active contact with the curved surface; Furthermore, a one-way valve is installed at each position on the oil inlet plate that is connected to each of the plunger holes, and the pressure oil passage is connected to multiple one-way valves through multiple oil holes on the oil supply shaft.

[0012] As one preferred embodiment, the clutch further includes a hydraulic coupling unit, which includes a pump wheel and a turbine that are interconnected. The pump wheel is connected to the cylinder block, and the turbine is connected to the outer casing. A low-pressure oil passage for injecting oil is provided on the oil supply shaft, and the low-pressure oil passage is connected to the pump wheel.

[0013] As one of the preferred embodiments, the pump wheel is sleeved inside the turbine, or the pump wheel and the turbine are arranged axially adjacent to each other.

[0014] As one of the preferred embodiments, the pressure oil passage is located at the center of the oil supply shaft, and the low-pressure oil passage is located outside the pressure oil passage, with at least two passages provided circumferentially.

[0015] As one preferred embodiment, the clutch further includes a coupling portion, which includes an outer gear sleeve and an inner gear sleeve. The outer gear sleeve is slidably connected to the outer periphery of the cylinder body via a spline, and the inner gear sleeve is disposed on the inner periphery of the outer housing and is axially movablely engaged with the outer gear sleeve. The outer toothed sleeve and the input shaft form a toothed sleeve engagement cavity, which is connected to the second chamber.

[0016] As one preferred embodiment, the joint further includes an external toothed sleeve return spring, which is connected between the external toothed sleeve and the step of the cylinder body.

[0017] Compared with the prior art, this application has the following advantages: The plunger-type hydrostatic clutch provided in this invention can reliably achieve the clutch function during power transmission. The clutch process is smooth and controllable, without significant impact. The rollers and the curved surfaces of the housing are in a well-lubricated state. Because the rollers can rotate along their own axis, the contact line between them and the housing is constantly changing. Therefore, the allowable contact pressure exceeds 100 MPa, far exceeding the allowable pressure of common friction plate clutches. Under the same friction diameter and friction coefficient, the friction force increases several times, thus increasing the transmittable torque. At the same time, because the curved surface of the housing has undulating curves, it acts like a spline, resulting in a significant reduction in overall radial dimensions and total weight compared to common friction plate clutches. Attached Figure Description

[0018] To more clearly illustrate the technical solution of this application, the drawings used in the description of this application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a front cross-sectional view of the plunger-type hydrostatic clutch in the engaged state according to an embodiment of this application; Figure 2 When the plunger-type hydrostatic clutch described in one embodiment of this application is in the engaged state, along Figure 1 Cross-sectional view along the AA direction; Figure 3 When the plunger-type hydrostatic clutch described in one embodiment of this application is in the disengaged state, along Figure 1 Cross-sectional view along the AA direction; Figure 4 This is a three-dimensional structural diagram of the plunger hydrostatic clutch after removing the outer shell, according to an embodiment of this application. Figure 5 This is a diagram showing the working state of the plunger-type hydrostatic clutch in the first stage according to an embodiment of this application; Figure 6 This is a diagram showing the working state of the plunger-type hydrostatic clutch in the second stage according to an embodiment of this application; Figure 7 This is a diagram showing the working state of the plunger-type hydrostatic clutch in the third stage according to an embodiment of this application; Figure 8 This is a diagram showing the working state of the plunger-type hydrostatic clutch in the fourth stage according to an embodiment of this application.

[0020] Explanation of reference numerals in the attached figures: 1. Input shaft; 2. Cylinder block; 3. Oil supply shaft; 4. Oil inlet plate; 5. Check valve; 6. Valve spring; 7. Piston bore; 8. Piston; 81. Compression spring; 9. Roller; 10. Exhaust slit; 11. Oil drain slit; 12. Trapping piston; 13. Piston spring; 14. Output shaft; 15. Housing; 151. Curved surface; 16. Pump wheel; 17. Turbine; 18. External gear sleeve; 19. Internal gear sleeve; 20. External gear sleeve return spring; 21. Spline; 22. External gear sleeve return spring. Detailed Implementation

[0021] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0022] Traditional friction clutches face significant technical bottlenecks in applications requiring high torque, small size, and high power density, making them unsuitable for applications such as new energy vehicles, electric drive systems, and high-speed equipment where lightweighting and compactness are paramount. While overrunning clutches can achieve high torque capacity under high engagement pressure thanks to high-strength metal contact pairs, their engagement process is instantaneous and self-locking, resulting in significant impact loads. Furthermore, they typically operate passively, making it impossible to achieve active and controllable engagement and disengagement processes based on system control requirements.

[0023] Therefore, it is necessary to provide a new clutch structure that, while ensuring high torque carrying capacity, breaks through the limitations of the allowable pressure of traditional friction materials, effectively reduces overall weight and volume while achieving high power density output; furthermore, the clutch should also be able to achieve controllable loading of engagement pressure, so that the engagement force can be gradually and smoothly established with the control signal, thereby avoiding violent impact at the moment of engagement and improving the stability and service life of the transmission system.

[0024] Based on the above requirements, this solution proposes a plunger-type hydrostatic clutch.

[0025] Reference Figures 1-3 As shown, Figure 1 This is a front cross-sectional view of the plunger-type hydrostatic clutch in the engaged state as shown in this invention. Figure 2 for Figure 1 Cross-sectional view along the AA direction. Figure 3 When the plunger-type hydrostatic clutch is in the disengaged state Figure 1A frontal cross-sectional view based on the AA side. A plunger-type hydrostatic clutch includes a hydrostatic clutch part, which includes a driving end, a driven end, and a transmission end. The transmission end is disposed on the driving end and is in movable contact with the driven end to separate or engage the driving end and the driven end. The driving end includes a cavity and an oil supply shaft 3. The cavity includes an inner cavity through which the oil supply shaft 3 passes and a cavity wall forming the inner cavity. The cavity wall has a plunger hole 7 and an oil discharge slit 11 that are interconnected. The oil supply shaft 3 has a pressure oil passage for injecting pressure oil. The driven end has a curved surface 151. The transmission end includes a one-way valve 5, which is disposed on the cavity and located at the position where the pressure oil passage and the plunger hole 7 are connected. The one-way valve 5 is used to control the flow of pressure oil between the pressure oil passage and the plunger hole 7. The system includes: a plunger 8, movably embedded in a plunger hole 7, with a groove on the side of the plunger 8 facing the curved surface 151, and a roller 9 rollingly embedded in the groove; an oil trapping piston 12, sleeved between the oil supply shaft 3 and the cavity wall, which movably divides the inner cavity into a first chamber and a second chamber, with the radial projection of the oil drain slit 11 falling into the first chamber; the second chamber is connected to the pressure oil passage and is used to drive the oil trapping piston 12 to move axially toward the first chamber under the action of pressure oil, thus blocking the oil drain slit 11; and a piston spring 13, disposed on the cavity and abutting against the oil trapping piston 12, which is used to drive the oil trapping piston 12 to move axially toward the second chamber when the pressure oil is stopped, thus connecting the oil drain slit 11 and the first chamber.

[0026] Specifically, the plunger-type hydrostatic clutch provided by this invention utilizes the oil-trapping working condition generated by the plunger 8 to obtain a high engagement pressure, thereby generating a large rotational resistance between the driving end and the driven end, thus achieving gradual synchronization between the driving end and the driven end. Simultaneously, the rollers 9 on the plunger 8 can be hydraulically controlled to generate a radial clamping force, enabling controllable contact between the driving end and the driven end. The driving end can generally be understood as the power input shaft 1 and the mating components supporting the driving end, or the driving end can be directly mounted onto the input shaft 1. The driving end has many structural forms, almost all including a cavity, cavity walls, and an inner cavity, serving as the structural support component of the entire driving end. The inner cavity forms a hydraulic working space, while the cavity walls protect the oil supply shaft 3, oil inlet plate 4, and oil-trapping piston 12, etc., within the inner cavity, and also serve as the mounting interface for other components (plunger 8, piston spring 13, etc.). The driven end can generally be understood as the power output shaft 14 and the force-transmitting component receiving the radial clamping force of the plunger 8. There are many structural forms for the active end. It is only necessary to design the force-transmitting component opposite to the plunger 8 to have a curved surface 151. The generatrix of the curved surface 151 can be set as an equal acceleration / deceleration curve or a cycloid function curve according to the working conditions.

[0027] For ease of description, the following example uses the fixed input shaft 1 and cylinder 2 as the active end cavity, and the fixed outer shell 15 and output shaft 14 as the passive end, to illustrate the structure of the present invention in detail. Of course, the positions of the input shaft 1 and output shaft 14 can be interchanged, with the outer shell 15 connected to the input shaft 1 as the active end, and the cylinder 2 connected to the output shaft 14 as the passive end; the remaining components can be configured accordingly. Both the input shaft 1 and output shaft 14 are hollow shafts, and the cylinder 2 is a hollow cylinder body 2. The hollow shaft cavity of the input shaft 1 and the hollow cavity of the cylinder body 2 together form the inner cavity. The outer shell 15 is approximately annular in shape, and the inner side of the outer shell 15 is composed of multiple evenly distributed curved surfaces 151 forming a closed curved surface 151. The following will use… Figure 1 Based on the orientation shown, the input shaft 1 is located on the left side of the cylinder body 2, and the output shaft 14 is located on the right side of the outer casing 15. The outer casing 15 is fitted over the right side portion of the input shaft 1 and the entire cylinder body 2. The cylinder body 2 extends inside the casing to the connecting step surface of the output shaft 14 and the outer casing 15.

[0028] Compared to the traditional active end, this embodiment features a supply shaft 3. The supply shaft 3 extends through the shaft cavity of the input shaft 1 into the cylinder cavity and extends to the right within the cylinder cavity, near the right end of the cylinder body 2. A pressure oil passage is formed inside the supply shaft 3, through which pressurized oil enters the cavity or the plunger hole 7. Specifically, the pressure oil passage extends parallel to the central axis of the supply shaft 3, and its extension length can be less than or nearly equal to the shaft length of the supply shaft 3. In this embodiment, the pressure oil passage is located at the axis of the supply shaft 3 and extends to near the right end face of the supply shaft 3, but does not penetrate the supply shaft 3. This embodiment allows the supply shaft 3 to be connected to an external hydraulic control system to control the injection and stop of pressurized oil, thereby achieving active control of the clutch.

[0029] A plunger hole 7 is formed on the outer side of the cylinder wall of the cylinder body 2. The thickness of the plunger hole 7 is less than the wall thickness of the cylinder body 2. A plunger 8 is installed in the plunger hole 7, and the plunger 8 is clearance-fitted with the plunger hole 7 on the cylinder body 2. The plunger 8 can be cylindrical, rectangular with rounded corners, or other shapes. The plunger 8 can slide radially back and forth in the plunger hole 7 of the cylinder body 2. A semi-circular groove is provided on the outer side of the plunger 8, and a cylindrical roller 9 is installed in the groove. The roller 9 can rotate in the groove. At the position of the cylinder body 2 where the plunger hole 7 is installed, an oil drain slit 11 is further formed on the cylinder wall. The oil drain slit 11 extends from the plunger hole 7 into the cylinder wall, so that the oil drain slit 11 communicates with both the plunger hole 7 and the cylinder cavity. In some embodiments, the axial length of the oil drain slit 11 can be less than the axial length of the plunger hole 7, the circumferential width is much smaller than the circumferential width of the plunger hole 7, and the radial thickness can be greater than, less than, or equal to the radial thickness of the plunger hole 7, etc. In some embodiments, after the plunger 8 is housed within the plunger bore 7, the cylindrical surface of the outer side of the roller 9 protrudes from the plunger bore 7, so that when the plunger 8 slides radially outward, the outer surface of the roller 9 can roll into contact with the outer casing 15.

[0030] An oil inlet plate 4 is provided inside the cylinder 2. The inner wall of the oil inlet plate 4 is fitted onto the oil supply shaft 3 located inside the cylinder cavity, while the outer wall is in close contact with the inner wall of the cylinder 2. The oil supply shaft 3 is indirectly secured in the inner cavity through the oil inlet plate 4. Of course, the oil supply shaft 3 can also be securely mounted in the cylinder cavity by additional bearings. In this embodiment, the oil supply shaft 3 has a first radial oil hole and a second radial oil hole spaced apart from left to right, and both radial oil holes are connected to the pressure oil passage. An oil passage is formed between the oil inlet plate 4 and the oil supply shaft 3. The oil passage can connect to the first radial oil hole and the plunger hole 7. Therefore, the inlet of the oil passage formed by the oil inlet plate 4 can connect to the pressure oil passage on the oil supply shaft 3 through the first radial oil hole, and the outlet of the oil passage connects to the plunger hole 7 on the cylinder 2. Therefore, a one-way valve 5 is installed on the oil inlet plate 4 at the position corresponding to the oil passage to prevent the pressure oil from leaving through the oil passage when the oil trapping piston 12 is in the compression stroke, thus preventing the oil trapping condition from being achieved. When the inlet oil pressure is greater than the internal pressure of cylinder 2, the one-way valve 5 opens, and the pressurized oil in the pressure oil passage can flow through the first radial oil hole to the oil passage and smoothly pass through the one-way valve 5 and then flow to the plunger hole 7. When the inlet oil pressure is less than the internal pressure of cylinder 2, the one-way valve 5 closes. After the oil trapping piston 12 completes the compression stroke and closes the oil discharge slit 11, the plunger hole 7 is in a relatively closed space. That is, when the plunger 8 in the plunger hole 7 moves inward to discharge oil, the pressurized oil will not flow out from the oil discharge slit 11, and at the same time, the pressurized oil will not be discharged from the oil passage where the one-way valve 5 is located, thus achieving the oil trapping condition.

[0031] In other embodiments, the oil inlet plate 4 may not be required inside the cylinder body 2. Instead, a portion of the oil inlet plate 4 can extend from the cylinder body 2 as a derivative component of the cylinder body 2 (which can be considered as part of the cylinder wall), and the one-way valve 5 can be directly mounted on this cylinder wall. By designing an independent oil inlet plate 4, the one-way valve 5 can be installed on the oil inlet plate 4, and then the oil inlet plate 4 can be assembled into the cylinder cavity.

[0032] It can be seen that the plunger hole 7 is a groove located on the outer side of the cylinder wall. Therefore, a third radial oil hole communicating with the plunger hole 7 can be opened on the inner side of the cylinder wall, and the oil passage outlet of the oil inlet plate 4 can be connected to the plunger hole 7 through the third radial oil hole. For example, the third radial oil hole is a straight hole, located on the cylinder wall at a position corresponding to the inner side of the plunger hole 7 and simultaneously corresponding to the outer side of the oil inlet plate 4.

[0033] The cylinder cavity is also equipped with a cup-shaped oil trapping piston 12 and a piston spring 13. The outer diameter of the oil trapping piston 12 slides against the inner wall of the cylinder. The oil trapping piston 12 can be located on the right side of the oil inlet plate 4 and is separated from the oil inlet plate 4 by the inner step of the cylinder body 2. One end of the piston spring 13 is connected to the inner step of the cylinder body 2, and the other end abuts against the oil trapping piston 12. The inner circumference of the oil trapping piston 12 is also sleeved on the oil supply shaft 3. The left side is the first chamber and the right side is the second chamber. The oil trapping piston 12 can move axially back and forth relative to the oil supply shaft 3, so the volume of the first chamber and the second chamber changes back and forth. The first chamber is set corresponding to the oil drain slit 11. Controlling the movement of the oil trapping piston 12 can gradually close the oil drain slit 11. When the oil drain slit 11 is completely closed, the first chamber is separated from the oil drain slit 11. Conversely, the first chamber is connected to the oil drain slit 11. The second chamber is connected to the second radial oil hole, so the second chamber can be connected to the pressure oil passage on the oil supply shaft 3 through the second radial oil hole.

[0034] Preferably, when no oil is being injected, the oil trapping piston 12 is located to the right of the oil drain slit 11 and just does not block the oil drain slit 11, and the axial length of the oil drain slit 11 is less than or equal to the axial length of the oil trapping piston 12. Therefore, when oil is being injected, the oil trapping piston 12 moves axially to the left, slowly blocking the oil drain slit 11, until it is completely blocked.

[0035] Preferably, the piston spring 13 is located in the first chamber, and the piston moves to the right by the thrust of the piston spring 13 after being compressed, thus isolating the piston spring 13 from the high-pressure oil. It can be understood that the piston spring 13 can also be located in the second chamber, and the piston moves to the right by the pulling force of the piston spring 13 after being pulled, thus resetting the oil-trapping piston 12.

[0036] Preferably, the inner side of the plunger 8 is provided with a venting slit 10 connecting the plunger hole 7 and the groove, so that the air in the plunger hole 7 can be discharged to the groove area connected to the outside through the venting slit 10 during the movement of the plunger 8, thereby realizing the venting function of the plunger hole 7 and avoiding the gas from affecting the movement of the plunger 8. In some embodiments, the venting slit 10 and the oil drain slit 11 can be staggered in the axial direction. It should be emphasized that both the venting slit 10 and the oil drain slit 11 are very narrow and have limited drainage capacity. Therefore, even if the venting slit 10 is connected to the outside, a small portion of the oil will overflow from the slit during oil injection. However, since the oil supply is much greater than the overflow, sufficient pressure will still be gradually built up inside the cylinder to push the plunger 8 to move.

[0037] The working process and principle of the clutch structure provided by this invention are as follows: When the cylinder 2, which is integrated with the input shaft 1, is in a rotating state, the rollers 9 on the plunger 8 are not in contact with the outer housing 15 when no pressurized oil is injected. Therefore, the power of the cylinder 2 cannot be transmitted to the outer housing 15, which is fixedly connected to the output shaft 14, and the clutch is in a disengaged state.

[0038] When clutch engagement is required, the external control system injects pressurized oil into the pressurized oil passage of the oil supply shaft 3. The pressure of the pressurized oil is regulated by the external control system through a pressure regulating system such as a proportional valve. The pressurized oil flows through the first radial oil hole to the oil inlet plate 4. When the pressure exceeds the spring force of the valve spring 6 of the one-way valve 5, the one-way valve 5 opens, and the oil enters the plunger hole 7 on the cylinder body 2. Because there is a small gap between the plunger 8 and the outer roller 9, and because there are narrow slits on the inner side of the plunger 8 and the inner side of the cylinder body 2, the gas in the plunger hole 7 is discharged through the exhaust slit 10 under the action of the pressurized oil, and the pressurized oil fills the plunger hole 7. As the pressure gradually increases, the plunger 8 moves radially outward until the roller 9 at the top of the plunger 8 is blocked by the inner curved surface 151 on the outer casing 15.

[0039] Since the cylinder body 2 and the input shaft 1 are integrated and in a rotating state, while the outer shell 15 and the output shaft 14 are fixedly connected and in a stationary state, the roller 9 moves along the function curve of the curved surface 151 on the inner side of the outer shell 15 under the pressure of the plunger 8, and rotates along its own axis under the action of friction. Since the curved surface 151 of the outer shell 15 is an equal acceleration / deceleration curve or other periodic function curve, the distance from each point to the rotation center of the cylinder body 2 is different and varies as a function. The movement of the roller 9 along the curved surface 151 of the outer shell 15 causes the plunger 8 connected to the roller 9 to produce periodic reciprocating motion relative to the plunger hole 7 of the cylinder body 2. When the plunger 8 moves radially outward, it is the oil suction stroke, and the pressurized oil enters the plunger hole 7 from the one-way valve 5 of the oil inlet plate 4; when the plunger 8 moves radially towards the rotation center, it is the oil discharge stroke, the one-way valve 5 closes, and the pressurized oil is discharged from the oil discharge slit 11 in the cylinder body 2.

[0040] The pressurized oil supplied by the oil supply shaft 3 simultaneously flows through the second radial oil hole to the second chamber located on the right side of the oil trapping piston 12. As the oil pressure gradually increases, the pressure on the oil trapping piston 12 gradually exceeds the spring force of the piston spring 13, pushing the oil trapping piston 12 to the left, gradually blocking the oil drain slit 11 until it is completely closed. As the oil drain slit 11 gradually closes, the plunger 8, which is forcibly pushed by the curved surface 151 of the outer casing 15, finds it increasingly difficult to discharge the oil from the plunger hole 7. The internal oil pressure continuously increases, causing the pressure of the plunger 8 acting on the inner curved surface 151 of the outer casing 15 through the roller 9 to continuously increase. Therefore, the friction also increases. Under the action of this friction, the outer casing 15 obtains torque, and the rotational speed continuously increases until it approaches the rotational speed of the cylinder 2, which is integrated with the input shaft 1, thus completing the engagement process.

[0041] Therefore, the clutch provided in this embodiment of the invention can reliably achieve the clutch function during power transmission. The clutch process is smooth and controllable, without significant impact. Both the roller 9 and the curved surface 151 of the outer shell 15 are made of alloy steel and are in a well-lubricated state. Because the roller 9 can rotate along its own axis, the contact line between it and the outer shell 15 is constantly changing. Therefore, the allowable contact pressure exceeds 100 MPa, far exceeding the allowable pressure of common friction plate clutches. Under the same friction diameter and friction coefficient, the friction force increases several times, thus increasing the transmittable torque. At the same time, since the curved surface 151 of the outer shell 15 is a curve with ups and downs, it plays a role similar to spline transmission. Compared with common friction plate clutches, the overall radial dimension and total weight are significantly reduced.

[0042] As a preferred design in this embodiment, the transmission end also includes a compression spring 81, which is fixed to the cavity wall and abuts against the plunger 8. In this embodiment, the compression spring 81 is installed on the cylinder 2. The compression spring 81 can be a separate type or an integral type. The compression spring 81 contacts the plunger 8 and applies radial pressure to the plunger 8, forcing the plunger 8 to retract into the plunger hole 7 inside the cylinder 2 when only subjected to centrifugal force. This prevents the rollers 9 inside the plunger 8 from contacting the curved surface 151 inside the outer casing 15. Therefore, when no pressurized oil is injected, the transmission part is separated from the driven end. When pressurized oil is injected, the plunger 8 in the cylinder 2 tends to slide radially outward under the action of centrifugal force. However, since the design pressure of the compression spring 81 is greater than the centrifugal force of the plunger 8, the plunger 8 does not produce radial movement. Therefore, the rollers 9 on the plunger 8 do not contact the outer casing 15. As pressurized oil fills the plunger orifice 7, and as the pressure increases, the plunger 8 overcomes the pressure of the compression spring 81 and moves radially outward until the roller 9 at the top of the plunger 8 is blocked by the curved surface 151 on the inner side of the housing 15.

[0043] As a preferred design of this embodiment, multiple plunger holes 7 and oil drain slits 11 are provided. Multiple plunger holes 7 are arranged at intervals along the circumference of the cylinder body 2 and are correspondingly connected to multiple oil drain slits 11. Each plunger hole 7 is correspondingly provided with a plunger 8, and each plunger 8 is correspondingly provided with a roller 9. Multiple rollers 9 are in active contact with the curved surface 151. In addition, a one-way valve 5 is installed at the position on the oil inlet plate 4 that is connected to each plunger hole 7. The pressure oil passage is connected to multiple one-way valves 5 through multiple first radial oil holes on the oil supply shaft 3.

[0044] In this embodiment, by arranging multiple plungers 8 evenly along the circumference, multiple rollers 9 apply contact pressure to the curved surface 151 during the oil discharge stroke, making the contact load distribution of the clutch more uniform. Correspondingly, multiple oil passages are formed on the oil inlet plate 4 at the positions communicating with each plunger hole 7, i.e., between the oil inlet plate 4 and the oil supply shaft 3. One-way valves 5 are provided at each of the multiple oil passages, so that the pressure oil passages on the oil supply shaft 3 are connected to each one-way valve 5 through multiple first radial oil holes, allowing pressure oil to enter multiple plunger holes 7 simultaneously, improving the power density and torque transmission stability of the clutch, and enabling the clutch to achieve a large torque transmission capacity with a smaller structural size.

[0045] Correspondingly, when an exhaust slit 10 and a compression spring 81 are designed, the number of exhaust slits 10 and compression springs 81 are set one-to-one with the number of plungers 8.

[0046] The plunger-type hydrostatic clutch of the present invention can be used alone or in combination with a hydraulic coupling part and / or a connecting part. In the initial stage of engagement, the reciprocating frequency of the plunger 8 in the plunger-type hydrostatic clutch is very high, which is the relative rotational speed multiplied by the number of evenly distributed curved surface 151 segments of the outer housing 15. When the speed difference between the input shaft 1 and the output shaft 14 of the plunger-type clutch is large, the reciprocating frequency of the plunger 8 is too high, easily generating significant noise and shortening its lifespan. To address this, in this embodiment of the invention, a hydraulic coupling part can be provided at the front end of the plunger-type hydrostatic clutch to increase the speed of the output shaft 14 in the initial stage of clutch engagement, thereby reducing the speed difference between the input shaft 1 and the output shaft 14.

[0047] In one provided technical solution, the hydraulic coupling unit includes a pump wheel 16 and a turbine 17 that are interconnected. The pump wheel 16 is connected to the cylinder 2, and the turbine 17 is connected to the outer casing 15. A low-pressure oil passage for injecting oil is provided on the oil supply shaft 3, and the low-pressure oil passage is connected to the pump wheel 16. The hydraulic coupling unit is mainly composed of components such as the pump wheel 16 and the turbine 17. The pump wheel 16 and the turbine 17 can be arranged side-by-side or inside-outside. The pump wheel 16 is fixedly connected to the cylinder 2, and the turbine 17 is fixedly connected to the outer casing 15. For example, the input shaft 1 is fixed to the left end of the cylinder 2, and the outer diameter of the input shaft 1 is smaller than the outer diameter of the cylinder 2, so that a step is formed at the connection between the two. The pump wheel 16 can be sleeved on the outer periphery of the input shaft 1 and connected to the left side of the step. The interior of the hydraulic coupling unit is connected to the low-pressure oil passage on the oil supply shaft 3. The pump wheel 16 and the turbine 17 form a relatively closed space, with a narrow slit or oil drain hole to communicate with the outside. For example, the input shaft 1 is provided with a fourth radial oil hole that communicates with the pump wheel 16, and the oil supply shaft 3 is also provided with a fifth radial oil hole that communicates with the low-pressure oil passage, so that the low-pressure oil passage is connected to the pump wheel 16 through the fourth radial oil hole and the fifth radial oil hole.

[0048] When the clutch disengages, under the control of the external hydraulic control system, the low-pressure oil passage on the oil supply shaft 3 is closed, and there is no oil inside the hydraulic coupling part. The residual oil from the previous engagement process has been discharged from the narrow slit or drain hole under the action of centrifugal force. Therefore, there is no liquid medium between the pump wheel 16 and the turbine 17, and thus no torque transmission. When the clutch engages, oil enters the hydraulic coupling part through the low-pressure oil passage on the oil supply shaft 3, and the instantaneous oil supply is large, far exceeding the leakage of the narrow slit and drain hole. The sealed space formed by the pump wheel 16 and the turbine 17 is filled with oil. The pump wheel 16, which is fixedly connected to the cylinder 2 and rotates at high speed, transmits part of the power to the turbine 17 through the oil, thereby driving the outer shell 15, which is fixedly connected to the turbine 17, to rotate. This gradually reduces the relative speed difference between the cylinder 2 and the outer shell 15, so that the reciprocating frequency of the plunger 8 is reduced when the plunger hydrostatic clutch is engaged, thus extending its service life. Meanwhile, the narrow slit on the hydraulic coupling part also guides the oil to flow to the joint between the roller 9 in the plunger-type hydrostatic clutch and the curved surface 151 of the outer casing 15, which plays a role in heat dissipation.

[0049] In a preferred embodiment, the pressure oil passage is located at the center of the oil supply shaft 3, and the low-pressure oil passage is located outside the pressure oil passage, with at least two passages arranged circumferentially. This embodiment arranges the low-pressure oil passages radially outside the pressure oil passages and sets up multiple passages. This allows for a more uniform and stable oil supply to the hydraulic coupling unit when oil is injected into the oil supply shaft 3, enabling the oil to enter the pump impeller 16 evenly circumferentially, thereby improving the stability of oil circulation within the hydraulic coupling unit. Simultaneously, by arranging the high-pressure and low-pressure oil passages in a radially layered manner, mutual interference between the high-pressure and low-pressure oil circuits is avoided. This ensures that the plunger-type hydrostatic clutch unit receives a stable high-pressure oil source while also ensuring a continuous low-pressure oil supply to the hydraulic coupling unit, thus achieving coordinated operation of the two transmission structures and improving the overall stability and reliability of the clutch operation.

[0050] After the plunger 8 clutch engages, to avoid the plunger 8 clutch operating under high pressure for extended periods, this embodiment can switch to a toothed engagement part, fixing the input shaft 1 (integrated with the cylinder body 2) and the output shaft 14 (connected to the outer casing 15) together, thus eliminating the reliance on the plunger 8 clutch for torque transmission. The toothed engagement part can be composed of components such as an outer toothed sleeve 18, an inner toothed sleeve 19, an outer toothed sleeve return spring 20, and a seal (not shown in the figure). Specifically, the engagement part includes an outer toothed sleeve 18 and an inner toothed sleeve 19. The outer toothed sleeve 18 is slidably connected to the outer circumference of the cylinder body 2 via a spline 21, and the inner toothed sleeve 19 is disposed on the inner circumference of the outer casing 15 and axially engages with the outer toothed sleeve 18. A toothed sleeve engagement cavity is formed between the outer toothed sleeve 18 and the input shaft 1, and this cavity communicates with a second chamber. Therefore, the outer toothed sleeve 18 is connected to the outer surface of the cylinder wall via a spline 21 and can move along the cylinder wall axis, while the inner toothed sleeve 19 is fixedly connected to the output shaft 14. Preferably, the left side of the cylinder wall is a cylindrical structure used to house the transmission end, while the right side forms a stepped structure. The outer gear sleeve 18 is disposed on this step, forming a gear sleeve engagement cavity with the stepped structure. The right side has a second chamber inside, which continues to communicate with the gear sleeve engagement cavity through a sixth radial oil hole on the cylinder wall. Therefore, when the plunger 8 type clutch is engaged, the relative speed difference between the input shaft 1 and the output shaft 14 is close to zero. The outer gear sleeve 18 can be pushed towards the inner gear sleeve 19 and enter the engagement state through hydraulic pressure or other actuating elements. The torque of the input shaft 1 is directly transmitted to the output shaft 14 through the engagement gear sleeve.

[0051] The structure and working principle of a plunger-type hydrostatic clutch of the present invention will be described in detail below with reference to specific embodiments.

[0052] like Figure 4 As shown, Figure 4 This is a three-dimensional structural diagram of a plunger-type hydrostatic clutch after removing the outer casing 15 and pressure spring 81, among other parts. (Refer to reference...) Figures 1-3A plunger-type hydrostatic clutch includes a hydrostatic clutch section, a hydraulic coupling section, and a engagement section, which together form three functional sections: a hydrostatic clutch section, a hydraulic coupling section, and a gear sleeve engagement section. The input shaft 1 is integral with the cylinder body 2, and the output shaft 14 is fixedly connected to the outer casing 15. A pump wheel 16 is located on the left side of the cylinder body 2 on the input shaft 1 and is fixedly connected to the cylinder body 2. A turbine 17 is fixedly connected to the outer casing 15. The pump wheel 16 and turbine 17 are arranged internally and externally, but can also be arranged left-right depending on the operating conditions. Ten plunger holes 7 are evenly distributed along the circumference of the cylinder body 2. Each plunger hole 7 is a rectangular hole with rounded corners. A third radial oil hole is opened on the left side of the interior of each plunger hole 7, communicating with an oil inlet plate 4. The oil inlet plate 4 is installed on an inner step inside the cylinder cavity. A one-way valve 5 is installed at the point where it communicates with the third radial oil hole of each plunger hole 7, or the one-way valve 5 is directly installed on the cylinder wall. Each plunger bore 7 contains a plunger 8, which is clearance-fitted to the plunger bore 7 and can slide radially along the cylinder body 2. The top of the plunger 8 is a semi-circular hole with a roller 9 installed on it. The roller 9 is clearance-fitted to the semi-circular hole of the plunger 8 and can rotate freely within the semi-circular hole. A venting slit 10 is opened at the bottom of the plunger 8, and an oil draining slit 11 is also opened on the inner side of the cylinder body 2 corresponding to the plunger bore 7. A compression spring 81 is installed on the outside of the cylinder body 2, and the compression spring 81 is in contact with the plunger 8, providing radial pressure to the plunger 8 towards the axis of the cylinder body 2.

[0053] The outer casing 15 is located around the cylinder body 2. The inner surface of the outer casing 15 is a closed curved surface 151 composed of three evenly distributed equal acceleration and deceleration curves. The right side of the cylinder body 2 has a stepped shaft and a spline 21. An outer gear sleeve 18 is mounted on the stepped shaft on the right side of the cylinder body 2 and is slidably connected to the stepped shaft via the spline 21, allowing it to move axially along the spline 21 on the cylinder body 2. The right side of the outer gear sleeve 18 has a step, where an outer gear sleeve return spring 20 is installed. The other end of the outer gear sleeve return spring 20 abuts against the stepped surface connecting the output shaft 14 and the outer casing 15. Inside the outer casing 15, on the right side, is an inner gear sleeve 19, integral with the outer casing 15. The cylinder body 2 is a hollow cavity. An oil-trapping piston 12 and a piston spring 13 are installed on the right side of the oil drain slit 11 within the inner cavity. When there is no pressurized oil supply, the piston spring 13 pushes the oil-trapping piston 12 to the right, and the oil drain slit 11 is not blocked by the oil-trapping piston 12. An oil supply shaft 3 is installed inside the cavity of cylinder block 2. The oil supply shaft 3 has low-pressure oil passages and high-pressure oil passages, and the oil supply is controlled by an external control system. The low-pressure oil passage leads to a closed cavity formed by the pump wheel 16 and turbine 17, and also communicates with the plunger hole 7 and the oil drain slit 11 inside cylinder block 2, serving as the oil drain channel for the plunger 8 and the trapped piston 12 on cylinder block 2 during operation. The high-pressure oil passage communicates with the oil inlet plate 4 installed inside cylinder block 2. When the pressure exceeds the pressure of the valve spring 6 of the one-way valve 5, oil can enter the plunger hole 7 of cylinder block 2 through the oil inlet plate 4. Simultaneously, the high-pressure oil flows to the second chamber on the right side of the trapped piston 12. When sufficient pressure is built up, the trapped piston 12 can be pushed to the left. The second chamber on the right side of the trapped piston 12 has a sixth radial oil hole, leading to the toothed sleeve engagement cavity formed by the outer toothed sleeve 18 and the stepped shaft of cylinder block 2. Once sufficient oil pressure is established, it can overcome the pressure of the outer gear sleeve return spring 20, pushing the outer gear sleeve 18 to move to the right and engage with the inner gear sleeve 19.

[0054] The entire clutch operation is controlled by an external hydraulic control system. When no oil enters the oil supply shaft 3, the cylinder 2, which is integrated with the input shaft 1, rotates at high speed. However, the plunger 8 is restricted by the plunger 8 spring and cannot move outward. The roller 9 at the top of the plunger 8 does not contact the curved surface 151 of the outer casing 15. There is also no oil in the hydraulic coupling part, so torque cannot be transmitted through oil. Under the action of the outer gear sleeve return spring 20, the engagement sleeve is on the left side. The outer gear sleeve 18 and the inner gear sleeve 19 are not in contact and cannot transmit torque. Figures 5-8 As shown, Figures 5-8 The diagrams show the working state of the clutch at different stages of operation. The black filled areas in the diagrams represent the oil-filled regions.

[0055] Please see Figure 5In the first stage, when the clutch begins to engage, oil enters the low-pressure oil passage of the oil supply shaft 3. The oil enters the sealed space formed by the pump wheel 16 and the turbine 17. Air in the space is discharged from the narrow gap between the pump wheel 16 and the turbine 17, and some oil also overflows from the narrow gap. However, because the oil supply volume is large, it far exceeds the amount of oil overflowing from the narrow gap. Therefore, the oil quickly fills the sealed space formed by the pump wheel 16 and the turbine 17. The oil is accelerated by the pump wheel 16 to gain higher kinetic energy, rushes towards the turbine 17, and drives the outer housing 15, which is integrated with the output shaft 14, to rotate. Under the action of hydraulic coupling, the speed difference between the output shaft 14 and the input shaft 1 gradually decreases. At the same time, the low-pressure oil passage fluid is also connected to the plunger hole 7 on the cylinder body 2 through the oil inlet plate 4 on the left side of the oil trapping piston 12. The low-pressure oil enters the plunger hole 7 of the cylinder body 2. Under the action of low oil pressure, the plunger 8 can overcome the pressure of the compression spring 81 and move radially outward. However, because the oil pressure is low and no oil trapping effect is formed, it basically does not transmit torque.

[0056] Please see Figure 6 In the second stage, after the relative speed difference between the output shaft 14 and the input shaft 1 decreases under the hydraulic coupling of the pump wheel 16 and the turbine 17, oil enters the pressure oil passage of the oil supply shaft 3. The pressure oil pressure is greater than the spring force of the valve spring 6 of the one-way valve 5 on the oil inlet plate 4, and the one-way valve 5 is opened. The pressure oil enters the plunger hole 7 of the cylinder 2 through the oil inlet plate 4, making the plunger 8 have greater pressure. The pressure acts on the roller 9, and the friction between the roller 9 and the outer shell 15 increases slightly, enhancing the torque transmission capability. At the same time, the pressure oil also enters the second chamber on the right side of the oil trapping piston 12 from the oil supply shaft 3, and enters the gear sleeve engagement cavity formed by the outer gear sleeve 18 and the stepped shaft of the cylinder 2 through the oil hole (sixth radial oil hole) on the right side of the oil trapping piston 12. The pressure oil pressure is controlled by the outside, and the initial pressure is low, which is insufficient to counteract the spring force that pushes the oil trapping piston 12 and the outer gear sleeve 18 to move axially.

[0057] Please see Figure 7In the third stage, as the external hydraulic control system gradually increases the oil pressure in the pressure oil circuit, the oil-trapping piston 12 overcomes the spring force and gradually moves to the left. The oil discharge slit 11 in the inner cavity of the cylinder 2 is gradually closed. At this time, the plunger 8 presses the roller 9 against the curved surface 151 of the outer shell 15 under the action of the pressure oil. As the cylinder 2 rotates relative to the outer shell 15, the movement of the roller 9 along the curved surface 151 of the outer shell 15 drives the plunger 8 to move radially back and forth along the plunger hole 7. When the plunger 8 moves outward, it is the oil suction process, and the pressure oil enters the plunger hole 7 through the one-way valve 5 on the oil inlet plate 4. When the plunger 8 moves inward under the constraint of the inner curved surface 151 of the outer shell 15, it is the oil discharge process. Due to the action of the one-way valve 5 on the oil inlet plate 4, the oil can only be discharged from the oil discharge slit 11. However, as the oil discharge slit 11 is gradually blocked by the oil-trapping piston 12 until it is closed, the oil discharge becomes more and more difficult as the slit is blocked, which causes the oil pressure inside the plunger hole 7 to rise. When the oil discharge slit 11 is completely blocked, the oil can only be discharged from the fitting clearance between the plunger 8 and the plunger hole 7. The oil pressure can rise to more than 30MPa, which means that the oil trapping condition occurs. The maximum pressure that can be achieved is related to the fitting clearance between the plunger 8 and the plunger hole 7.

[0058] As the pressure increases, the pressure applied by the plunger 8 between the roller 9 and the curved surface 151 of the outer casing 15 gradually increases. The tangential component of the pressure between the roller 9 and the curved surface 151 of the outer casing 15 relative to the rotation center of the cylinder 2, and the tangential component of the frictional force generated by the pressure, form a torque transmission, driving the outer casing 15 to rotate faster until the rotational speeds of the outer casing 15 and the cylinder 2 are basically the same, completing the engagement action. At this time, the pressure oil pressure acting on the inner side of the outer gear sleeve 18 in the gear sleeve engagement cavity is still insufficient to overcome the initial force of the outer gear sleeve return spring 20, and cannot push the outer gear sleeve 18 to move axially.

[0059] Please see Figure 8 In the fourth stage, when the input shaft 1 and output shaft 14, i.e., the cylinder 2 and outer casing 15, rotate at approximately synchronized speeds, the external control system continues to increase the oil pressure in the pressure oil circuit. This allows the oil pressure acting in the gear sleeve engagement cavity to overcome the spring force of the outer gear sleeve return spring 20, pushing the outer gear sleeve 18 to slide to the right. The outer teeth on the outer gear sleeve 18 and the inner teeth on the inner gear sleeve 19 on the outer casing 15 enter a locking state. Since the outer gear sleeve 18 and the cylinder 2 are slidably connected via spline 21, the power on the cylinder 2 is directly transmitted to the outer casing 15. Power transmission no longer requires the assistance of the hydraulic coupling part and hydrostatic parts such as plunger 8 and roller 9, completing the entire switching process. The low-pressure oil passage no longer supplies oil, and the residual oil between the pump wheel 16 and turbine 17 chambers is discharged through the narrow gap between the pump wheel 16 and turbine 17 under centrifugal force. At the same time, the pressure oil passage continues to supply oil to maintain the engagement state.

[0060] When separation is required, the pressure in the pressure oil passage is reduced until the oil supply to the pressure oil passage is shut off. The oil pressure in the gear sleeve engagement cavity is less than the spring force of the outer gear sleeve return spring 20. The outer gear sleeve 18 is pushed to the left by the spring, and the outer teeth on the outer gear sleeve 18 separate from the inner teeth on the inner gear sleeve 19 on the outer shell 15. The plunger 8 in the plunger hole 7 on the cylinder 2 is pushed back to the bottom of the plunger hole 7 by the compression spring 81. The roller 9 no longer contacts the curved surface 151 of the outer shell 15. All torque transmission routes are interrupted, and the clutch enters the disengaged state.

[0061] It should be noted that the various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0062] In this document, the terms "upper," "lower," "left," "right," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are used only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations, nor should they be construed as indicating or implying relative importance. Moreover, the term "comprising" or any other variation thereof is intended to cover non-exclusive inclusion, such that a process, method, article, or terminal device that comprises a list of elements includes not only those elements, but also other elements not expressly listed, or elements inherent to such a process, method, article, or terminal device.

Claims

1. A plunger-type hydrostatic clutch, characterized in that, It includes a hydrostatic clutch, which includes a driving end, a driven end, and a transmission end. The transmission end is disposed on the driving end and is in movable contact with the driven end so that the driving end and the driven end can be separated or engaged. The active end includes a cavity and an oil supply shaft. The cavity includes an inner cavity through which the oil supply shaft passes and a cavity wall forming the inner cavity. The cavity wall has interconnected plunger holes and oil discharge slits. The oil supply shaft has a pressure oil passage for injecting pressure oil. The passive end has a curved surface. The transmission end includes: A one-way valve is provided on the cavity and located at the position where the pressure oil passage and the plunger hole are connected, for controlling the flow of pressure oil between the pressure oil passage and the plunger hole; A plunger is movably fitted into the plunger hole, and a groove is provided on the side of the plunger facing the curved surface, in which a roller is rolled and fitted. An oil trapping piston is sleeved between the oil supply shaft and the cavity wall, and movably divides the inner cavity into a first chamber and a second chamber; the oil discharge slit is provided corresponding to the first chamber, and the second chamber is connected to the pressure oil passage, which is used to drive the oil trapping piston to move axially towards the first chamber under the action of pressure oil, thereby blocking the oil discharge slit; A piston spring is disposed on the cavity and abuts against the oil trapping piston, used to drive the oil trapping piston to move axially toward the second chamber when the pressure oil injection is stopped, thereby connecting the oil discharge slit and the first chamber.

2. A plunger-type hydrostatic clutch according to claim 1, characterized in that, The plunger has a narrow venting slit on its inner side that connects the plunger hole and the groove.

3. A plunger-type hydrostatic clutch according to claim 1, characterized in that, The transmission end also includes a compression spring, which is fixed to the cavity wall and abuts against the plunger.

4. A plunger-type hydrostatic clutch according to any one of claims 1-3, characterized in that, The cavity includes an input shaft and a cylinder, which are fixedly connected; the passive end includes a fixed outer shell and an output shaft, the outer shell is sleeved on the outer periphery of the cavity, and the inner side of the outer shell is composed of multiple evenly distributed curved surfaces forming a closed curved surface.

5. A plunger-type hydrostatic clutch according to claim 4, characterized in that, The plunger holes and the oil drain slits are provided in multiple ways. The multiple plunger holes are arranged at intervals along the circumference of the cylinder body and are correspondingly connected to the multiple oil drain slits. Each plunger hole is provided with a plunger, and each plunger is provided with a roller. The multiple rollers are in active contact with the curved surface. Furthermore, a one-way valve is installed at each position on the oil inlet plate that connects to each of the plunger holes, and the pressure oil passage is connected to multiple one-way valves through multiple oil holes on the oil supply shaft.

6. A plunger-type hydrostatic clutch according to claim 4, characterized in that, The clutch also includes a hydraulic coupling unit, which includes a pump wheel and a turbine that are connected to each other. The pump wheel is connected to the cylinder block, and the turbine is connected to the outer casing. A low-pressure oil passage for injecting oil is provided on the oil supply shaft, and the low-pressure oil passage is connected to the pump wheel.

7. A plunger-type hydrostatic clutch according to claim 6, characterized in that, The pump wheel is fitted inside the turbine, or the pump wheel and the turbine are arranged axially adjacent to each other.

8. A plunger-type hydrostatic clutch according to claim 4, characterized in that, The clutch also includes an engagement portion, which includes an outer gear sleeve, an inner gear sleeve, and an outer gear sleeve return spring. The outer gear sleeve is slidably connected to the outer periphery of the cylinder body via a spline. The inner gear sleeve is disposed on the inner periphery of the outer housing and is axially movablely engaged with the outer gear sleeve. The outer gear sleeve return spring is connected between the outer gear sleeve and the step of the cylinder body. The outer toothed sleeve and the input shaft form a toothed sleeve engagement cavity, which is connected to the second chamber.

9. A plunger-type hydrostatic clutch according to claim 1, characterized in that, The transmission end includes an oil inlet plate, which is sleeved between the oil supply shaft and the cavity wall, and the one-way valve is disposed on the oil inlet plate.

10. A plunger-type hydrostatic clutch according to claim 1, characterized in that, The cavity includes an input shaft and an outer shell, which are fixedly connected; the passive end includes a fixedly connected cylinder and an output shaft.

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