A clutch suitable for use in a hydro-automatic transmission

Abstract

The present application relates to a clutch, in particular to a clutch suitable for a hydraulic automatic transmission, which solves the problem that the existing clutch has only one torque output end, and when the transmission assembly connected with the clutch needs multiple torque output ends, the existing clutch cannot meet the requirement, the present application comprises a first outer hub, a connecting disc, a first inner hub and a second outer hub which are coaxially arranged in sequence in the first outer hub, a piston seat is coaxially arranged in the first outer hub, and the connecting disc is connected with the first outer hub; further comprising a first coupling assembly and a second coupling assembly, the first coupling assembly is arranged between the first outer hub, the piston seat, the first inner hub and the connecting disc, and is used for coupling and transmitting the torque of the piston seat to the first inner hub; the second coupling assembly is arranged between the first coupling assembly, the piston seat and the second outer hub, and is used for coupling and transmitting the torque of the piston seat to the second outer hub.

Description

Technical Field

[0001] This invention relates to clutches, and more particularly to a clutch suitable for hydraulic automatic transmissions. Background Technology

[0002] An automatic transmission (AT) is a type of transmission that automatically selects the appropriate gear based on engine conditions, as opposed to a manual transmission. An AT primarily consists of three parts: a torque converter, a planetary gear transmission mechanism, and an electro-hydraulic control system. The torque converter fundamentally simplifies gear shifting and also functions similarly to the clutch in a traditional manual transmission. The planetary gear transmission mechanism is mainly composed of several planetary gear sets mounted on shafts and a shift actuator. By separating or engaging different components within the shift actuator, various gear ratios can be achieved, thus realizing gear changes. The electro-hydraulic control system is used for locking up the torque converter, controlling gear shifting, and ensuring shift quality.

[0003] Currently, commonly used gear shifting actuators generally include clutches, brakes, and one-way clutches. Among them, the clutch, as a key component of the gear shifting actuator, is mainly composed of hub-type parts, pistons, and friction pairs. Its performance directly affects the power output of the vehicle's powertrain. Existing clutches typically have only one torque output end connected to the transmission components. For example, Chinese invention patent CN110701207B discloses a clutch integrated structure, which includes an integrated input hub, gear ring, clutch, clutch support, piston, and power take-off input shaft, and is provided with a working oil passage and a lubrication oil passage. When power is transmitted from the engine to the input hub, the working oil passage is filled with high-pressure oil and reaches the piston chamber, pushing the piston to press the clutch, thus disengaging the clutch and transmitting power to the power take-off input shaft. At the same time, when the clutch is closed, the clutch lubrication oil passage opens, and lubricating oil reaches the clutch to lubricate the friction plates. Similarly, when the friction plates do not need to transmit torque, the piston returns to its original position and the lubrication oil passage closes, thereby reducing the drag loss of the clutch and improving efficiency. However, this clutch structure ultimately outputs torque only through the power take-off input shaft. If the transmission components connected to the clutch require the clutch to have multiple torque output ends to meet the power transmission needs, the clutch integrated structure disclosed in the aforementioned invention patent cannot meet the requirements. Summary of the Invention

[0004] The purpose of this invention is to solve the problem that existing clutches have only one torque output end, and cannot meet the requirements when the transmission components connected to the clutch require the clutch to have multiple torque output ends. The invention provides a clutch suitable for hydraulic automatic transmissions.

[0005] To achieve the above-mentioned objectives, the present invention provides the following technical solution:

[0006] A clutch suitable for a hydraulic automatic transmission is characterized in that it includes a first outer hub, a first inner hub, a second outer hub, a connecting plate, a first coupling assembly, a second coupling assembly, and a piston seat;

[0007] The piston seat is coaxially disposed inside the first outer hub and is fixedly connected to the first outer hub; the connecting plate, the first inner hub, and the second outer hub are coaxially disposed inside the first outer hub from the outside to the inside, and the connecting plate is connected to the first outer hub by a spline; the output end of the connecting plate is connected to a spline sleeve, the spline sleeve is coaxially disposed inside the spline sleeve, the output shaft is connected to the output end of the first inner hub, and the piston seat is coaxially disposed inside the piston seat, the bushing is connected to the output end of the second outer hub;

[0008] The first coupling assembly is disposed between the first outer hub, the piston seat, the first inner hub, and the connecting plate, and is used to couple the torque of the piston seat to the first inner hub;

[0009] The second coupling assembly is disposed between the first coupling assembly, the piston seat, and the second outer hub, and is used to couple the torque of the piston seat to the second outer hub.

[0010] Furthermore, the first coupling assembly includes a first piston disposed between the first outer hub and the piston seat, and a first retaining ring disposed on the inner wall of the first outer hub. The first piston and the first retaining ring are connected by a first return spring. A plurality of first mating plates are connected on the inner wall of the first outer hub and outside the first retaining ring. A plurality of first friction plates are connected on the outer surface of the first inner hub. The plurality of first friction plates and the first mating plates are alternately disposed between the first outer hub and the connecting disc. The space between the first piston and the first outer hub forms a first oil cavity. The first oil passage outlet on the piston seat is connected to the first oil cavity. When the oil fills the first oil cavity, the first piston will squeeze the first mating plates and the first friction plates to make them fit together.

[0011] The second coupling assembly includes a second piston disposed between the first piston and the piston seat, and a second retaining ring disposed on the outer wall of the piston seat. The second retaining ring and the second piston are connected by a second return spring. Multiple second mating plates are connected on the inner wall of the second outer hub and outside the second retaining ring. Multiple second friction plates are connected on the outer wall of the piston seat. The multiple second friction plates and the second mating plates are alternately arranged between the first piston and the second outer hub. The space between the second piston and the first piston forms a second oil cavity. The outlet of the second oil passage on the piston seat is connected to the second oil cavity. When the oil fills the second oil cavity, the second piston will squeeze the second mating plates and the second friction plates to make them fit together.

[0012] Furthermore, a balance piston is provided between the first piston and the piston seat. The balance piston is located on the inner side of the second retaining ring. A through hole is provided on the balance piston. The extrusion head of the second piston, which is used to extrude the second mating plate and the second friction plate, is provided corresponding to the through hole. A second abutment boss is provided on the second piston. One end of the second return spring is connected to the second abutment boss, and the other end is connected to the inner side of the second retaining ring through the balance piston.

[0013] The first piston is provided with a first abutting boss, and a spring support plate is provided on the inner side of the first retaining ring. One end of the first return spring is connected to the first abutting boss, and the other end is connected to the inner side of the first retaining ring through the spring support plate.

[0014] Furthermore, the first piston has a first radial oil passage hole along the radial direction, which corresponds to the first return spring; the first outer hub has a first outer hub oil passage hole along the radial direction, which corresponds to the first return spring; the second piston has a second radial oil passage hole along the radial direction, which corresponds to the second return spring; and a third oil passage is provided on the piston seat. The third oil passage, the second radial oil passage hole, the first radial oil passage hole, and the first outer hub oil passage hole constitute a spring cooling oil passage.

[0015] Furthermore, a fourth oil passage is provided on the piston seat, which corresponds to the second friction plate. A second outer hub radial oil passage is provided on the second outer hub in the radial direction corresponding to the position of the second mating plate. A first inner hub radial oil passage is provided on the first inner hub in the radial direction corresponding to the position of the first friction plate. The fourth oil passage, the second outer hub radial oil passage, and the first inner hub radial oil passage constitute the clutch plate cooling oil passage, and the outlet of the first inner hub radial oil passage is connected to the first outer hub oil passage.

[0016] Furthermore, a fifth oil passage is provided on the piston seat, and axial oil passages are provided on the second outer hub, the first inner hub, and the connecting plate. The fifth oil passage and the axial oil passages on the second outer hub, the first inner hub, and the connecting plate constitute the lubrication oil circuit of the transmission assembly.

[0017] Furthermore, a first thrust bearing is provided between the spline sleeve and the output shaft, a second thrust bearing is provided between the output shaft and the second outer hub, and a third thrust bearing is provided between the second outer hub and the piston seat.

[0018] Furthermore, the piston seat has a sixth oil passage along the axial direction. The inlets of the fourth and fifth oil passages are both connected to the sixth oil passage, and the outlet of the sixth oil passage is set to correspond to the third thrust bearing. The sixth oil passage constitutes a bearing cooling oil passage.

[0019] Furthermore, a first sealing ring is provided between the first piston and the first outer hub, a second sealing ring is provided between the piston seat and the first piston, a third sealing ring is provided between the second piston and the first piston, a fourth sealing ring is provided between the balance piston and the first piston, and a fifth sealing ring is provided between the second piston and the piston seat.

[0020] Furthermore, a third retaining ring and a fourth retaining ring are provided on the inner wall of the first outer hub, and a fifth retaining ring is provided on the outer wall of the piston seat. The third retaining ring abuts against the first mating plate located on the outermost side to limit the axial position of the first friction plate and the first mating plate. The fourth retaining ring is located between the connecting disc and the first outer hub to limit the axial position of the connecting disc and the first outer hub. The fifth retaining ring abuts against the second friction plate located on the outermost side to limit the axial position of the second friction plate and the second mating plate.

[0021] Compared with the prior art, the beneficial effects of the present invention are:

[0022] (1) The present invention provides a clutch suitable for a hydraulic automatic transmission, comprising a first outer hub, a first inner hub, a second outer hub, a connecting plate, a first coupling assembly, a second coupling assembly, and a piston seat. The piston seat is coaxially disposed within the first outer hub and fixedly connected to the first outer hub. The connecting plate, the first inner hub, and the second outer hub are sequentially coaxially disposed within the first outer hub. A spline sleeve is connected to the output end of the connecting plate. An output shaft is coaxially disposed within the spline sleeve and connected to the output end of the first inner hub. A bushing is coaxially disposed inside the piston seat and connected to the output end of the second outer hub. The present invention can achieve the following four torque output modes:

[0023] ① When the torque of the piston seat is transmitted to the first outer hub, and neither the first coupling assembly nor the second coupling assembly is working, the torque of the piston seat will be coupled to the connecting plate because the first outer hub is connected to the connecting plate by a spline, and then the torque will be output through the spline sleeve.

[0024] ② When the first coupling component is working and the second coupling component is not working, the torque of the piston seat will be coupled to the first inner hub and then to the output shaft. At this time, the spline sleeve and the output shaft output torque together.

[0025] ③ When the second coupling component is working while the first coupling component is not working, the torque of the piston seat will be coupled to the second outer hub and then to the bushing. At this time, the splined sleeve and the bushing output torque together.

[0026] ④ When the first coupling component and the second coupling component work together, the torque of the piston seat will be coupled and transmitted to the connecting plate, the first inner hub and the second outer hub respectively. At this time, the torque will be output by the spline sleeve, the output shaft and the bushing together.

[0027] This solves the problem that existing clutches only have one torque output end, making it impossible to provide multiple torque outputs to meet the transmission requirements of the connected transmission components.

[0028] (2) The clutch provided by the present invention is suitable for hydraulic automatic transmission. By setting up a spring cooling oil circuit, the heat generated by the first return spring and the second return spring during operation is carried away, ensuring the reliability of the spring operation; by setting up a clutch plate cooling oil circuit, the heat generated by the friction between the friction plate and the mating plate can be carried away, preventing problems such as adhesion, material shedding, and deformation caused by excessive temperature; by setting up a transmission component lubrication oil circuit, the oil can flow out from the axial oil passage and then flow to the transmission component connected to the clutch for lubrication; by setting up a bearing cooling oil circuit, the heat generated by the third thrust bearing during operation can be carried away, ensuring the reliability of the bearing operation.

[0029] (3) The clutch for a hydraulic automatic transmission provided by the present invention is equipped with a spring support plate and a balance piston. Because the size of the first retaining ring and the second retaining ring is limited, it is difficult to directly connect the first return spring to the inner side of the first retaining ring. Therefore, a spring support plate is set on the inner side of the first retaining ring to increase the connection area and reduce the connection difficulty. The function of the balance piston is the same as that of the spring support plate. Since the second retaining ring is set on the piston seat and the second return spring is far away from the second retaining ring, a balance piston is set on the inner side of the second retaining ring to increase the connection area. In order not to block the second piston from squeezing the second mating plate and the second friction plate, a through hole is opened on the balance piston. The squeezing head of the second piston is set corresponding to the through hole. This reduces the connection difficulty of the second return spring and does not hinder the normal movement of the second piston.

[0030] (4) The clutch of the present invention, applicable to a hydraulic automatic transmission, is provided with a third retaining ring and a fourth retaining ring on the inner wall of the first outer hub and a fifth retaining ring on the outer wall of the piston seat. The third retaining ring abuts against the first mating plate located on the outermost side and is used to limit the axial position of the first friction plate and the first mating plate, so as to prevent the first friction plate and the first mating plate from causing unnecessary friction with the connecting plate when squeezed by the first piston, thus causing damage. The fourth retaining ring is located between the connecting plate and the first outer hub and is used to limit the axial position of the connecting plate and the first outer hub, so as to prevent the connecting plate from moving axially during rotation and thus causing wear with the first outer hub. The fifth retaining ring abuts against the second friction plate located on the outermost side and is used to limit the axial position of the second friction plate and the second mating plate, so as to prevent the second friction plate and the second mating plate from causing unnecessary friction with the second outer hub when squeezed by the second piston. Attached Figure Description

[0031] Fig. 1 This is a cross-sectional view of an embodiment of the clutch of the present invention applicable to a hydraulic automatic transmission;

[0032] Fig. 2 This is a schematic diagram of the oil circuit structure in an embodiment of the present invention;

[0033] The annotations in the attached figures are explained as follows:

[0034] 1-First outer hub, 101-First outer hub oil passage hole; 2-Connecting plate, 201-Connecting plate axial oil passage hole; 3-First inner hub, 301-First inner hub radial oil passage hole, 302-First inner hub axial oil passage hole; 4-Second outer hub, 41-Second outer hub radial oil passage hole, 42-Second outer hub axial oil passage hole; 5-Piston seat, 51-First oil passage, 52-Second oil passage, 53-Third oil passage, 54-Fourth oil passage, 55-Fifth oil passage, 56-Sixth oil passage; 6-Spline sleeve, 7-Output shaft, 8-Shaft sleeve, 9-First piston, 91-First radial oil passage hole; 10-First return spring, 11-The... 12-First mating plate, 13-First friction plate, 14-Second piston, 141-Second radial oil passage hole; 15-Second return spring, 16-Second retaining ring, 17-Balance piston, 18-Second mating plate, 19-Second friction plate, 20-Spring support plate, 21-First thrust bearing, 22-Second thrust bearing, 23-Third thrust bearing, 24-Third retaining ring, 25-Fourth retaining ring, 26-First sealing ring, 27-Second sealing ring, 28-Third sealing ring, 29-Fourth sealing ring, 30-Fifth sealing ring, 31-Fifth retaining ring, 32-First oil chamber, 33-Second oil chamber. Detailed Implementation

[0035] The present invention will be further described below with reference to the accompanying drawings and exemplary embodiments.

[0036] Reference Figs. 1-2 The present invention provides a clutch for a hydraulic automatic transmission, comprising a first outer hub 1, a connecting disc 2, a first inner hub 3, a second outer hub 4, and a piston seat 5. The piston seat 5 is coaxially disposed within the first outer hub 1 and is welded to the first outer hub 1 by electron beam welding. The connecting disc 2, the first inner hub 3, and the second outer hub 4 are coaxially disposed within the first outer hub 1 from the outside to the inside.

[0037] The first outer hub 1 and the connecting disc 2 are connected by a spline. To prevent the connecting disc 2 from moving axially and rubbing against the first outer hub 1 during rotation, a fourth retaining ring 25 is provided between the first outer hub 1 and the connecting disc 2. The fourth retaining ring 25 is located in a retaining ring groove opened on the inner wall of the first outer hub 1. This simple structure restricts the axial position of the connecting disc 2 and the first outer hub 1. A spline sleeve 6 is welded to the output end of the connecting disc 2 by electron beam welding. The spline sleeve 6 can be connected to the transmission assembly to transmit torque.

[0038] A first piston 9 is provided between the first outer hub 1 and the piston seat 5. The first piston 9 and the first outer hub 1 are connected by a spline engagement. A retaining ring groove is provided on the inner wall of the first outer hub 1, and a first retaining ring 11 is provided in the retaining ring groove. A first return spring 10 is provided between the first retaining ring 11 and the first piston 9. In order to connect the first return spring 10 to the first piston 9 and the first retaining ring 11 respectively, a first abutting boss is provided on the first piston 9. One end of the first return spring 10 is connected to the first abutting boss. However, the first retaining ring 11 is very small, and there are too few places that can be used for connection. In order to increase the connection area with the first return spring 10, a spring support plate 20 is provided on the inner side of the first retaining ring 11. The spring support plate 20 is also connected to the first outer hub 1 by a spline engagement. In this way, the other end of the first return spring 10 can be connected to the spring support plate 20. The first retaining ring 11 and the first return spring 10 are indirectly connected by the spring support plate 20, which simplifies the connection difficulty.

[0039] Multiple first mating plates 12 are splinedly connected to the inner wall of the first outer hub 1 and located outside the first retaining ring 11. Multiple first friction plates 13 are splinedly connected to the outer surface of the first inner hub 3. In this embodiment, four first mating plates 12 are arranged axially, and three first friction plates 13 are arranged axially. Multiple first friction plates 13 and first mating plates 12 are alternately arranged between the first outer hub 1 and the connecting disk 2. The first mating plate 12 is closest to the first piston 9. Thus, each first friction plate 13 is located between two adjacent first mating plates 12. In order to limit the axial position of the first friction plate 13 and the first mating plate 12 and prevent unnecessary friction between them and the connecting disk 2 during the compression of the first piston 9, a third retaining ring 24 is provided on the inner wall of the first outer hub 1. The third retaining ring 24 abuts against the first mating plate 12 located on the outermost side. Thus, during the compression of the first piston 9, the third retaining ring 24 will limit the axial position of the first friction plate 13 and the first mating plate 12.

[0040] To provide power for the movement of the first piston 9, a first oil passage 51 is provided on the piston seat 5. The space between the first piston 9 and the first outer hub 1 forms a first oil chamber 32. The outlet of the first oil passage 51 is connected to the first oil chamber 32. When the oil fills the first oil chamber 32, the first piston 9 will squeeze the first mating plate 12 and the first friction plate 13 to make them fit together. In this way, the torque of the piston seat 5 will be transmitted to the first outer hub 1 first, and then transmitted to the first inner hub 3 through the fit of the first friction plate 13 and the first mating plate 12. The output end of the first inner hub 3 is welded with an output shaft 7 by electron beam welding. The output shaft 7 is coaxially arranged in the spline sleeve 6, so that torque can be output through the output shaft 7. When the output shaft 7 is not required to output torque, the oil in the first oil chamber 32 is drained, and the first piston 9 will be reset under the elastic force of the first return spring 10. The first friction plate 13 will disengage from the first mating plate 12. A first sealing ring 26 is provided between the first piston 9 and the first outer hub 1, and a second sealing ring 27 is provided between the piston seat 5 and the first piston 9. These two sealing rings can ensure that the oil pressure will not leak after the oil enters the first oil chamber 32, thus ensuring the reliability of the movement of the first piston 9.

[0041] A second piston 14 is provided between the first piston 9 and the piston seat 5. A second retaining ring 16 is provided on the outer wall of the piston seat 5. The second retaining ring 16 is located in a retaining ring groove opened on the outer wall of the piston seat 5. In order to facilitate the connection of the second return spring 15, a second abutment boss is provided on the second piston 14. A balance piston 17 is provided on the inner side of the second retaining ring 16 to increase the connection area. In order not to block the second piston 14 from pressing the second mating plate 18 and the second friction plate 19, a through hole is opened on the balance piston 17. The pressing head of the second piston 14 is set corresponding to the through hole. One end of the second return spring 15 is connected to the second abutment boss, and the other end is connected to the balance piston 17. In this way, it is indirectly connected to the inner side of the second retaining ring 16, which reduces the connection difficulty of the second return spring 15 and does not hinder the normal movement of the second piston 14.

[0042] Multiple second mating plates 18 are splinedly connected to the inner wall of the second outer hub 4 and located outside the second retaining ring 16. Multiple second friction plates 19 are splinedly connected to the outer wall of the piston seat 5. In this embodiment, four second mating plates 18 are arranged axially, and five second friction plates 19 are arranged axially. The multiple second friction plates 19 and second mating plates 18 are alternately arranged between the first piston 9 and the second outer hub 4. The first second friction plate 19 is closest to the second piston 14. Thus, each second mating plate 18 is located between two adjacent second friction plates 19. In order to limit the axial position of the second friction plates 19 and the second mating plates 18 and prevent unnecessary friction with the second outer hub 4 when they are squeezed by the second piston 14, a fifth retaining ring 31 is provided on the outer wall of the piston seat 5. The fifth retaining ring 31 abuts against the second friction plate 19 located on the outermost side. During the squeezing process of the second piston 14, the fifth retaining ring 31 will limit the axial position of the second friction plates 19 and the second mating plates 18.

[0043] To provide power to the second piston 14, a second oil passage 52 is provided on the piston seat 5. The space between the second piston 14 and the first piston 9 forms a second oil chamber 33. The outlet of the second oil passage 52 is connected to the second oil chamber 33. When the second oil chamber 33 is filled with oil, the second piston 14 will squeeze the second mating plate 18 and the second friction plate 19 to make them fit together. In this way, the torque of the piston seat 5 will be transmitted to the second outer hub 4 through the second friction plate 19 and the second mating plate 18. A bushing 8 is welded to the output end of the second outer hub 4 by electron beam welding. The bushing 8 is located inside the piston seat 5 and is coaxial with the piston seat 5. An internal spline is provided inside the bushing 8, so that... Torque is transmitted to the corresponding transmission components through bushing 8. When the bushing 8 is not needed for torque output, the oil in the second oil chamber 33 is drained, and the second piston 14 is reset under the elastic force of the second return spring 15. The second friction plate 19 and the second mating plate 18 are disengaged. A third sealing ring 28 is provided between the second piston 14 and the first piston 9, a fourth sealing ring 29 is provided between the balance piston 17 and the first piston 9, and a fifth sealing ring 30 is provided between the second piston 14 and the piston seat 5. Through these three sealing rings, it can be ensured that the oil pressure will not leak after the oil enters the second oil chamber 33, thereby improving the reliability of the movement of the second piston 14.

[0044] To restrict the axial position of the spline sleeve 6, a first thrust bearing 21 is provided between the spline sleeve 6 and the output shaft 7. To restrict the axial position of the output shaft 7 and the second outer hub 4, a second thrust bearing 22 is provided between the output shaft 7 and the second outer hub 4. To restrict the axial position of the second outer hub 4 and the piston seat 5, a third thrust bearing 23 is provided between the second outer hub 4 and the piston seat 5. Through the mutual cooperation between the thrust bearings, the axial position of each component is limited, and axial movement will not easily occur during rotation, thus preventing friction between them.

[0045] The clutch provided by this invention can achieve the following four torque output methods:

[0046] ① When the torque of the piston seat 5 is transmitted to the first outer hub 1, and the first oil chamber 32 and the second oil chamber 33 are not filled with oil, because the first outer hub 1 and the connecting plate 2 are connected by a spline, the torque of the piston seat 5 will be coupled and transmitted to the connecting plate 2 after passing through the first outer hub 1, and then the torque will be output through the spline sleeve 6.

[0047] ② When the first oil chamber 32 is filled with oil while the second oil chamber 33 is not filled with oil, the first piston 9 will overcome the elastic force of the first return spring 10 under the action of oil pressure and squeeze the first mating plate 12 and the first friction plate 13. After the two are in contact, the torque of the piston seat 5 will be coupled and transmitted to the first inner hub 3, and then to the output shaft 7. At this time, the spline sleeve 6 and the output shaft 7 jointly output torque.

[0048] ③ When the second oil chamber 33 is filled with oil while the first oil chamber 32 is not filled with oil, the second piston 14 will overcome the elastic force of the second return spring 15 under the action of oil pressure and squeeze the second mating plate 18 and the second friction plate 19. After the two are in contact, the torque of the piston seat 5 will be coupled and transmitted to the second outer hub 4, and then to the bushing 8. At this time, the spline sleeve 6 and the bushing 8 output torque together.

[0049] ④ When both the second oil chamber 33 and the first oil chamber 32 are filled with oil, the first piston 9 and the second piston 14 move simultaneously. The torque of the piston seat 5 will be coupled and transmitted to the connecting plate 2, the first inner hub 3 and the second outer hub 4 respectively. At this time, the spline sleeve 6, the output shaft 7 and the bushing 8 will output torque together.

[0050] like Fig. 2As shown, the present invention also provides multiple oil passages, including a spring cooling oil passage for cooling the first return spring 10 and the second return spring 15. The spring cooling oil passage includes a third oil passage 53 opened on the piston seat 5, a second radial oil passage 141 opened on the second piston 14 along the radial direction, the second radial oil passage 141 being set corresponding to the second return spring 15, and a first radial oil passage 91 opened on the first piston 9 along the radial direction, the first radial oil passage 91 being set corresponding to the first return spring 10. In this way, the oil flows in from the third oil passage 53, passes through the second radial oil passage 141 and the first radial oil passage 91 in sequence, and finally flows out from the first outer hub oil passage 101. During the oil flow process, the heat generated by the reciprocating motion of the first return spring 10 and the second return spring 15 can be carried away, ensuring the reliability of the return spring operation.

[0051] During frictional coupling, the first friction plate 13 and the first mating plate 12, as well as the second friction plate 19 and the second mating plate 18, will rub against each other due to the difference in rotational speed. If the heat generated during this friction cannot be dissipated in time, it will cause the friction plates and mating plates to stick together. In severe cases, it will lead to problems such as the friction material falling off and structural deformation. Therefore, the present invention also designs a clutch plate cooling oil circuit, which includes a fourth oil passage 54 opened on the piston seat 5. The fourth oil passage 54 is set corresponding to the second friction plate 19. Since the friction plates and the coupling plates are alternately arranged in the axial direction, in order to better cool, three fourth oil passages 54 are evenly distributed along the axial direction. In this way, when the oil flows, it will flow evenly through all the first friction plates 13 and the first mating plates 12, ensuring that each first friction plate 13 and the first mating plate 12 can be cooled by the oil. A second outer hub radial oil passage hole 41 is radially formed on the second outer hub 4, corresponding to the position of the second mating plate 18. A first inner hub radial oil passage hole 301 is radially formed on the first inner hub 3, corresponding to the position of the first friction plate 13. Similarly, to accommodate all the second friction plates 19 and the second mating plates 18, three second outer hub radial oil passage holes 41 and three first inner hub radial oil passage holes 301 are evenly distributed axially. The outlet of the first inner hub radial oil passage hole 301 is connected to the first outer hub radial oil passage hole 301. With the hole 101 connected, when the oil flows sequentially through the fourth oil passage 54, the second outer hub radial oil passage 41, and the first inner hub radial oil passage 301, the first friction plate 13 and the first mating plate 12, as well as the second friction plate 19 and the second mating plate 18, are all immersed in the oil. The heat generated by friction will be absorbed by the oil. After absorbing the heat, the oil will flow through the gap between the splines on the first outer hub 1 that mate with each component to the first outer hub oil passage 101, and then flow out from the first outer hub oil passage 101.

[0052] The transmission components connected to the clutch also require oil lubrication during operation, so a transmission component lubrication oil circuit is also provided, which includes a fifth oil passage 55 opened on the piston seat 5, a second outer hub axial oil passage 42 opened along the second outer hub 4, a first inner hub axial oil passage 302 opened along the first inner hub 3, and a connecting plate axial oil passage 201 opened along the connecting plate 2. The oil enters from the fifth oil passage 55, flows through the second outer hub axial oil passage 42 and the first inner hub axial oil passage 302 in sequence, and finally flows out from the connecting plate axial oil passage 201 to lubricate the transmission components that need lubrication.

[0053] The third thrust bearing 23 restricts the axial position of the second outer hub 4 and the piston seat 5. During the clutch operation, the piston seat 5 is always rotating, which means that the third thrust bearing 23 is also always in operation. During the rotation of the bearing, a lot of heat is generated due to friction. If the temperature is too high, it will cause problems such as wear-resistant material falling off and structural deformation. Therefore, a bearing cooling oil circuit is also provided, which includes a sixth oil passage 56 opened axially on the piston seat 5. The inlets of the fourth oil passage 54 and the fifth oil passage 55 are all connected to the sixth oil passage 56, and the outlet of the sixth oil passage 56 is set to the third thrust bearing 23. The sixth oil passage 56 constitutes a bearing cooling oil circuit, so that oil can flow from the sixth oil passage 56 into the third thrust bearing 23, immersing it in oil and carrying away the heat generated by friction, ensuring the reliability of the third thrust bearing 23.

[0054] The embodiments described above are merely illustrative of specific implementations of the present invention and are not intended to limit the scope of the present invention. Various modifications and improvements made to the technical solutions of the present invention by those skilled in the art without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. A clutch suitable for a hydraulic automatic transmission, characterized in that: It includes a first outer hub (1), a first inner hub (3), a second outer hub (4), a connecting plate (2), a first coupling assembly, a second coupling assembly, and a piston seat (5); The piston seat (5) is coaxially arranged inside the first outer hub (1) and fixedly connected to the first outer hub (1); the connecting plate (2), the first inner hub (3), and the second outer hub (4) are coaxially arranged inside the first outer hub (1) from the outside to the inside, and the connecting plate (2) is connected to the first outer hub (1) by a spline; the output end of the connecting plate (2) is connected to a spline sleeve (6), and an output shaft (7) is coaxially arranged inside the spline sleeve (6), and the output shaft (7) is connected to the output end of the first inner hub (3); a bushing (8) is coaxially arranged inside the piston seat (5), and the bushing (8) is connected to the output end of the second outer hub (4); The first coupling assembly is disposed between the first outer hub (1), piston seat (5), first inner hub (3) and connecting plate (2) for coupling the torque of piston seat (5) to the first inner hub (3). The second coupling assembly is disposed between the first coupling assembly, the piston seat (5), and the second outer hub (4) for coupling the torque of the piston seat (5) to the second outer hub (4). The first coupling assembly includes a first piston (9) disposed between the first outer hub (1) and the piston seat (5), and a first retaining ring (11) disposed on the inner wall of the first outer hub (1). The first piston (9) and the first retaining ring (11) are connected by a first return spring (10). Multiple first mating plates (12) are connected on the inner wall of the first outer hub (1) and outside the first retaining ring (11). Multiple first friction plates (13) are connected on the outer surface of the first inner hub (3). Multiple first friction plates (13) and first mating plates (12) are alternately disposed between the first outer hub (1) and the connecting plate (2). The space between the first piston (9) and the first outer hub (1) forms a first oil cavity (32). The outlet of the first oil passage (51) on the piston seat (5) is connected to the first oil cavity (32). When the oil fills the first oil cavity (32), the first piston (9) will squeeze the first mating plates (12) and the first friction plates (13) to make them fit together. The second coupling assembly includes a second piston (14) disposed between the first piston (9) and the piston seat (5), and a second retaining ring (16) disposed on the outer wall of the piston seat (5). The second retaining ring (16) and the second piston (14) are connected by a second return spring (15). Multiple second mating plates (18) are connected on the inner wall of the second outer hub (4) and outside the second retaining ring (16). Multiple second friction plates (19) are connected on the outer wall of the piston seat (5). The multiple second friction plates (19) and the second mating plates (18) are alternately disposed between the first piston (9) and the second outer hub (4). The space between the second piston (14) and the first piston (9) forms a second oil chamber (33). The outlet of the second oil passage (52) on the piston seat (5) is connected to the second oil chamber (33). When the oil fills the second oil chamber (33), the second piston (14) will squeeze the second mating plates (18) and the second friction plates (19) to make them fit together.

2. The clutch for a hydraulic automatic transmission according to claim 1, characterized in that: A balance piston (17) is provided between the first piston (9) and the piston seat (5). The balance piston (17) is located on the inner side of the second retaining ring (16). A through hole is provided on the balance piston (17). The second piston (14) is used to squeeze the extrusion head of the second mating plate (18) and the second friction plate (19) and is provided corresponding to the through hole. A second abutting boss is provided on the second piston (14). One end of the second return spring (15) is connected to the second abutting boss, and the other end is connected to the inner side of the second retaining ring (16) through the balance piston (17). The first piston (9) is provided with a first abutting boss, and a spring support plate (20) is provided on the inner side of the first retaining ring (11). One end of the first return spring (10) is connected to the first abutting boss, and the other end is connected to the inner side of the first retaining ring (11) through the spring support plate (20).

3. The clutch for a hydraulic automatic transmission according to claim 1 or 2, characterized in that: The first piston (9) has a first radial oil passage (91) in the radial direction, which corresponds to the first return spring (10); the first outer hub (1) has a first outer hub oil passage (101) in the radial direction, which corresponds to the first return spring (10); the second piston (14) has a second radial oil passage (141) in the radial direction, which corresponds to the second return spring (15); the piston seat (5) has a third oil passage (53), which, the third oil passage (53), the second radial oil passage (141), the first radial oil passage (91), and the first outer hub oil passage (101) constitute the spring cooling oil passage.

4. The clutch for a hydraulic automatic transmission according to claim 3, characterized in that: The piston seat (5) is provided with a fourth oil passage (54), which is provided in relation to the second friction plate (19). The second outer hub (4) is provided with a second outer hub radial oil passage (41) in the radial direction in relation to the position of the second mating plate (18). The first inner hub (3) is provided with a first inner hub radial oil passage (301) in the radial direction in relation to the position of the first friction plate (13). The fourth oil passage (54), the second outer hub radial oil passage (41), and the first inner hub radial oil passage (301) constitute the clutch plate cooling oil passage, and the outlet of the first inner hub radial oil passage (301) is connected to the first outer hub oil passage (101).

5. The clutch for a hydraulic automatic transmission according to claim 4, characterized in that: The piston seat (5) is provided with a fifth oil passage (55), and axial oil passages are provided on the second outer hub (4), the first inner hub (3) and the connecting plate (2) along the axial direction. The fifth oil passage (55) together with the axial oil passages on the second outer hub (4), the first inner hub (3) and the connecting plate (2) constitute the lubrication oil circuit of the transmission component.

6. The clutch for a hydraulic automatic transmission according to claim 5, characterized in that: A first thrust bearing (21) is provided between the spline sleeve (6) and the output shaft (7), a second thrust bearing (22) is provided between the output shaft (7) and the second outer hub (4), and a third thrust bearing (23) is provided between the second outer hub (4) and the piston seat (5).

7. The clutch for a hydraulic automatic transmission according to claim 6, characterized in that: The piston seat (5) has a sixth oil passage (56) along the axial direction. The inlets of the fourth oil passage (54) and the fifth oil passage (55) are connected to the sixth oil passage (56), and the outlet of the sixth oil passage (56) is set to the third thrust bearing (23). The sixth oil passage (56) constitutes the bearing cooling oil passage.

8. The clutch for a hydraulic automatic transmission according to claim 7, characterized in that: A first sealing ring (26) is provided between the first piston (9) and the first outer hub (1), a second sealing ring (27) is provided between the piston seat (5) and the first piston (9), a third sealing ring (28) is provided between the second piston (14) and the first piston (9), a fourth sealing ring (29) is provided between the balance piston (17) and the first piston (9), and a fifth sealing ring (30) is provided between the second piston (14) and the piston seat (5).

9. The clutch for a hydraulic automatic transmission according to claim 8, characterized in that: The inner wall of the first outer hub (1) is provided with a third retaining ring (24) and a fourth retaining ring (25), and the outer wall of the piston seat (5) is provided with a fifth retaining ring (31). The third retaining ring (24) abuts against the first mating plate (12) located on the outermost side, and is used to limit the axial position of the first friction plate (13) and the first mating plate (12). The fourth retaining ring (25) is located between the connecting plate (2) and the first outer hub (1), and is used to limit the axial position of the connecting plate (2) and the first outer hub (1). The fifth retaining ring (31) abuts against the second friction plate (19) located on the outermost side, and is used to limit the axial position of the second friction plate (19) and the second mating plate (18).

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