Planetary gear system and double clutch thereof

Abstract

The planetary gear system comprises a sun gear, a planet gear, a gear ring, a planet carrier and a planet gear gasket, a special-shaped groove is formed in a planet shaft hole of the planet carrier, the planet gear gasket is clamped in the special-shaped groove, and a planet shaft of the planet gear penetrates through the planet gear gasket to be arranged in the planet shaft hole of the planet carrier. The special-shaped groove is formed in the planet carrier, the planet wheel gasket is clamped in the special-shaped groove, so that the planet wheel gasket does not move along with rotation of the planet wheel under the condition that the planet wheel rotates, and the planet wheel gasket does not move along with rotation of the planet wheel under the condition that the planet wheel rotates. According to the planetary gear system, abrasion cannot be generated between the planetary gear gasket and the planetary carrier, so that the planetary carrier can be made of light materials, the cost and the weight of the planetary carrier are reduced, and the cost and the weight of the planetary gear system are further reduced.

Description

Technical Field

[0001] The present application relates to the technical field of vehicle transmissions, and in particular to a planetary gear system and a dual clutch thereof. Background Art

[0002] The planetary gear and clutch of the transmission are key components of the transmission, and play an important role in the speed ratio change and gear shifting of the transmission. In recent years, car manufacturers have had increasingly higher requirements for lightweight, integrated and cost-reduced transmission parts.

[0003] However, the planet carriers of the current planetary gear system (planetary gear) are all made of steel, which is heavy. The steel planet carriers are machined from forged billets, and the manufacturing cost is also high. Summary of the invention

[0004] The purpose of the present application is to provide a planetary gear system and a dual clutch thereof, which are used to solve the problems of heavy weight and high cost caused by the planetary carrier of the current planetary gear set being made of steel.

[0005] In the first aspect, the present invention provides a planetary gear system, which includes a sun gear, a planetary gear, a ring gear, a planetary carrier and a planetary gear gasket; a special-shaped groove is opened at the planetary shaft hole of the planetary carrier, and the planetary gear gasket is clamped in the special-shaped groove, and the planetary shaft of the planetary wheel passes through the planetary gear gasket and is arranged in the planetary shaft hole of the planetary carrier, so as to rotatably fix the planetary wheel on the planetary carrier, and the planetary gear gasket is used to remain stationary when the planetary wheel rotates; the sun gear is used to drive the planetary carrier to move when it rotates itself; the planetary carrier is used to drive the planetary wheels to rotate when it moves itself; the planetary wheels are used to drive the ring gear to rotate when they rotate themselves, so as to output transmission force through the ring gear.

[0006] The planetary gear system designed as above has a special-shaped groove formed on the planet carrier and the planetary wheel gasket is clamped in the special-shaped groove. In this way, when the planetary wheel rotates, the planetary wheel gasket will not move with the rotation of the planetary wheel, and no wear will occur between the planetary wheel gasket and the planetary carrier. In this way, the planetary carrier can be made of lightweight materials, thereby reducing the cost and weight of the planetary carrier, and further reducing the cost and weight of the planetary gear system.

[0007] In an optional embodiment of the first aspect, the special-shaped groove includes a first special-shaped groove and a second special-shaped groove; the planetary gear gasket includes a first gasket and a second gasket, the first gasket is clamped in the first special-shaped groove, the second gasket is clamped in the second special-shaped groove, and the planetary gear is arranged between the first gasket and the second gasket.

[0008] In the above implementation mode, planetary wheel gaskets are arranged on the upper and lower sides of the planetary wheel, so that when the planetary wheel rotates, the planetary wheel gaskets on the upper and lower sides will not move with the rotation of the planetary wheel, so that no wear will occur between the planetary wheel gaskets on the upper and lower sides of the planetary wheel and the planetary carrier.

[0009] In an optional embodiment of the first aspect, each gasket is provided with a first through hole; the first through hole corresponds to the planetary shaft hole of the planetary carrier; the planetary shaft of the planetary wheel passes through the first through hole and is arranged in the planetary shaft hole of the planetary carrier to rotatably fix the planetary wheel on the planetary carrier.

[0010] In an optional embodiment of the first aspect, the planetary carrier also includes a first oil hole and a second oil hole; the first oil hole and the second oil hole are symmetrically distributed on both sides of the planetary shaft hole, and each gasket is provided with a second through hole and a third through hole, the second through hole corresponds to the first oil hole, and the third through hole corresponds to the second oil hole.

[0011] In the above implementation mode, the present scheme designs a second through hole and a third through hole on the first gasket, the second through hole corresponds to the first oil hole, and the third through hole corresponds to the second oil hole, so that the planetary gear gasket will not block the lubrication oil path at the meshing position of the planetary gear and the sun gear, thereby reducing the wear between the planetary gear and the sun gear and improving the reliability of the operation of the planetary gear and the sun gear.

[0012] In an optional embodiment of the first aspect, the first through hole includes a first circular hole and a first slot hole and a second slot hole connected to the first circular hole; the first slot hole and the second slot hole are symmetrically arranged, and the aperture of the first circular hole is the same as that of the planetary shaft hole; the first slot hole and the second slot hole are used for the transmission oil to flow out to lubricate the meshing position of the planetary gear and the sun gear.

[0013] In the above implementation mode, the first through hole designed in this scheme can not only fix the planetary shaft through the first circular hole, but also let the transmission oil flow out through the first slot hole and the second slot hole connected to the first circular hole, so that the planetary gear gasket will not block the lubrication of the meshing position of the planetary gear and the sun gear, thereby reducing the wear between the planetary gear and the sun gear, and improving the reliability and life of the planetary gear and the sun gear.

[0014] In an optional implementation of the first aspect, the special-shaped groove is a diamond-shaped groove, and the planetary wheel gasket is a diamond-shaped gasket.

[0015] In the above implementation manner, the present solution enables the diamond-shaped gasket to be more effectively clamped in the diamond-shaped groove by cooperating with the diamond-shaped groove and the diamond-shaped gasket, thereby more effectively reducing the probability of wear between the planetary wheel gasket and the planetary carrier.

[0016] In an optional embodiment of the first aspect, the first end of the planetary shaft is semi-cylindrical, and the planetary carrier includes a fixed protrusion; the first end of the planetary shaft faces the center of the planetary carrier, and the first end of the planetary shaft is fixed with the fixed protrusion to achieve radial limiting fixation of the planetary shaft.

[0017] In the above-mentioned implementation mode, the first end of the planetary shaft of the planetary gear array designed in this scheme is a semi-cylindrical structure, which cooperates with the fixed protrusion of the planetary frame to realize the radial limitation of the planetary shaft, so that the planetary shaft does not need to be fixed with additional devices (such as cylindrical pins, etc.), making the planetary shaft of this scheme easy to install and reducing the components of the planetary gear system, saving costs.

[0018] In an optional embodiment of the first aspect, the planetary gear system also includes a planetary carrier cover, and a planetary shaft oil channel is opened in the planetary shaft; the planetary carrier cover is used to block the transmission oil flowing out of the sun gear oil channel, so that the transmission oil passes through the cover and enters the planetary shaft oil channel and then flows to the meshing position of the planetary wheel and the ring gear to achieve gear lubrication.

[0019] In the above-mentioned implementation mode, the present scheme blocks the transmission oil flowing out of the sun gear oil passage through the planetary carrier cover, so that the blocked transmission oil flows to the meshing position of the planetary gear and the ring gear to achieve gear lubrication, thereby reducing the wear of the planetary gear and the ring gear, and improving the reliability and life of the planetary gear and the ring gear.

[0020] In an optional implementation of the first aspect, the material used to make the planet carrier includes cast aluminum material.

[0021] In the above implementation mode, the planet carrier is designed to be made of cast aluminum material, thereby reducing the weight and cost of the planet carrier of this solution.

[0022] In a second aspect, the present invention provides a dual clutch, which includes a planetary gear system according to any optional embodiment of the first aspect.

[0023] The dual clutch designed as above includes the planetary gear system of the first aspect. Therefore, the designed dual clutch can be provided with a special-shaped groove on the planet carrier and the planetary wheel gasket is clamped in the special-shaped groove. In this way, when the planetary wheel rotates, the planetary wheel gasket will not move with the rotation of the planetary wheel, so that no wear will occur between the planetary wheel gasket and the planetary carrier. In this way, the planetary carrier can be made of lightweight materials, thereby reducing the cost and weight of the planetary carrier, and further reducing the cost and weight of the dual clutch.

[0024] Other features and advantages of the present application will be described in detail in the subsequent detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0026] Figure 1 The overall three-dimensional structure diagram of the planetary gear system provided in the embodiment of the present application;

[0027] Figure 2 A first partial three-dimensional structural diagram of a planetary gear system provided in an embodiment of the present application;

[0028] Figure 3 An overall cross-sectional structural diagram of a planetary gear system provided in an embodiment of the present application;

[0029] Figure 4 A schematic diagram of the overall structure of the planet carrier provided in an embodiment of the present application;

[0030] Figure 5 A schematic diagram of the structure of the planetary gear and the gasket provided in the embodiment of the present application;

[0031] Figure 6 A structural diagram of a planetary gear gasket provided in an embodiment of the present application;

[0032] Figure 7 A schematic diagram of the structure of a planet carrier provided in an embodiment of the present application without gaskets and planetary gears installed;

[0033] Figure 8 A schematic diagram of the structure of a planetary shaft provided in an embodiment of the present application;

[0034] Fig. 9 A schematic diagram of the installation structure of the planetary shaft provided in an embodiment of the present application;

[0035] Fig.10 A second partial three-dimensional structural diagram of a planetary gear system provided in an embodiment of the present application;

[0036] Fig.11 A schematic diagram of the oil circuit arrangement structure provided in an embodiment of the present application;

[0037] Fig.12 A schematic diagram of the structure of the dual clutch provided in an embodiment of the present application.

[0038] Icons: 10-sun gear; 20-planetary gear; 210-planetary shaft; 2110-first end; 2120-planetary shaft oil passage; 30-gear ring; 40-planet carrier; 410-planetary shaft hole; 420-special-shaped groove; 4210-first special-shaped groove; 4220-second special-shaped groove; 430-first oil hole; 440-second oil hole; 450-fixing protrusion; 50-planetary gear gasket; 510-first gasket; 520-second gasket; 5110-first through hole; 51110-first circular hole; 51120-first slot hole; 51130-second slot hole; 5120-second through hole; 5130-third through hole; 60-planet carrier cover; 70-transmission input shaft; 80-needle bearing; a-first oil channel of transmission input shaft; b-second oil channel of transmission input shaft; c-oil channel of clutch A inner hub; d-oil channel of sun gear; A-first clutch; A1-first clutch supporting piston; A2-first clutch driving piston; A3-first clutch steel plate; A4-first clutch friction plate; A5-first clutch inner hub body; A6-first clutch outer hub; B-second clutch; B1-second clutch driving piston; B2-second clutch supporting piston; B3-second clutch steel plate; B4-second clutch friction plate; B5-second clutch inner hub body; B6-second clutch outer hub. DETAILED DESCRIPTION

[0039] In order to make the purpose, technical scheme and advantages of the embodiments of the present application clearer, the technical scheme in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all of the embodiments. The components of the embodiments of the present application described and shown in the drawings here can be arranged and designed in various different configurations.

[0040] In the description of this application, it should be noted that the terms "inside", "outside", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of the application is usually placed when in use, which is only for the convenience of describing this application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application. In addition, the terms "first", "second", etc. are only used to distinguish the description, and cannot be understood as indicating or implying relative importance.

[0041] In the description of this application, it should also be noted that, unless otherwise clearly specified and limited, the terms "disposed" and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0042] The planetary gear and clutch of the transmission are key components of the transmission, and play an important role in the speed ratio change and gear shifting of the transmission. In recent years, car manufacturers have had increasingly higher requirements for lightweight, integrated and cost-reduced transmission parts.

[0043] However, the planet carriers of the current planetary gear system (planetary gear) are all made of steel, which is heavy. The steel planet carriers are machined from forged billets, and the manufacturing cost is also high.

[0044] Based on the above problems, the present application designs a planetary gear system and a dual clutch. By opening a special-shaped groove on the planetary carrier, the planetary wheel gasket is clamped in the special-shaped groove, so that when the planetary wheel rotates, the planetary wheel gasket will not move with the rotation of the planetary wheel, so that there will be no wear between the planetary wheel gasket and the planetary carrier, so that the planetary carrier can be made of lightweight materials, such as cast aluminum materials, etc., thereby reducing the cost and weight of the planetary carrier, and further reducing the cost and weight of the planetary gear system. At the same time, the planetary shaft end of the planetary wheel designed in this scheme adopts a semi-cylindrical structure, and there is a convex structure corresponding to the position of the cast aluminum planetary carrier. The planetary shaft is fixed by rotating the semi-cylindrical structure of the planetary shaft and clamping the convex structure of the planetary carrier position, thereby realizing the radial limit of the planetary shaft; in addition, the present scheme presses the planetary carrier cover through the planetary carrier, and the lubrication of the planetary wheels and bearings is lubricated by the sun gear rebounding through the planetary carrier cover, thereby improving the lubrication degree of the planetary wheels and bearings.

[0045] Based on the above ideas, the present application first provides a planetary gear system. Figure 1 This is the overall three-dimensional structure diagram of the planetary gear system. Figure 2 It is a partial three-dimensional structure diagram of the planetary gear system. Figure 3 This is the overall cross-sectional structure diagram of the planetary gear system. Figure 4 For the schematic diagram of the planet carrier structure, please refer to Figure 1 , Figure 2 , Figure 3 as well as Figure 4The planetary gear system includes a sun gear 10, a planetary gear 20, a ring gear 30, a planetary carrier 40 and a planetary gear gasket 50. A special-shaped groove 420 is opened at the planetary shaft hole 410 of the planetary carrier, and the planetary gear gasket 50 is clamped in the special-shaped groove 420. The planetary shaft 210 of the planetary gear 20 passes through the planetary gear gasket 50 and is set in the planetary shaft hole 410 of the planetary carrier 40.

[0046] The planetary gear system designed above is mainly used to change the transmission ratio to adapt to different gear requirements. For example, the planetary gear system can be applied to an automatic transmission of an automobile, which realizes the switching of multiple gears of the vehicle through the cooperation of the sun gear, the planetary gear, the planetary carrier and the ring gear. Specifically, in the planetary gear system designed above, when working, the sun gear 10 itself rotates to drive the planetary carrier 40 to move, the planetary carrier 40 moves to drive the planetary gear 20 to rotate, and the planetary gear 20 rotates to drive the ring gear 30 to rotate, thereby realizing the output of the transmission force through the ring gear 30, and the fixed or rotating state of the ring gear 30 determines the rotation direction and speed of the output shaft.

[0047] Among them, when the planetary gear system designed as above is working, since the planetary wheel gasket 50 designed in this scheme is stuck in the special-shaped groove 420, when the planetary wheel 20 rotates, the planetary wheel gasket 50 will not move relative to the planetary carrier 40, that is, the planetary wheel gasket 50 will not move with the rotation of the planetary wheel 20, so that the rotational friction between the planetary wheel gasket 50 and the planetary carrier 40 causes wear, so that the planetary carrier can be made of lightweight materials.

[0048] As a possible implementation, the planet carrier 40 may be made of cast aluminum or other metal materials that are lighter and cheaper than steel, such as alloy materials.

[0049] The planetary gear system designed as above has a special-shaped groove formed on the planet carrier and the planetary wheel gasket is clamped in the special-shaped groove. In this way, when the planetary wheel rotates, the planetary wheel gasket will not move with the rotation of the planetary wheel, and no wear will occur between the planetary wheel gasket and the planetary carrier. In this way, the planetary carrier can be made of lightweight materials, thereby reducing the cost and weight of the planetary carrier, and further reducing the cost and weight of the planetary gear system.

[0050] In the optional implementation of this embodiment, please refer to Figure 5The special-shaped groove 420 designed in the present application may include a first special-shaped groove 4210 and a second special-shaped groove 4220, and the first special-shaped groove 4210 and the second special-shaped groove 4220 may be distributed on the upper and lower sides of the planetary gear 20. In this case, the planetary gear gasket 50 designed in the present scheme may include a first gasket 510 and a second gasket 520, the first gasket 510 is clamped in the first special-shaped groove 4210, the second gasket 520 is clamped in the second special-shaped groove 4220, and the planetary gear 20 is arranged between the first gasket 510 and the second gasket 520.

[0051] In the above embodiment, planetary wheel gaskets are arranged on the upper and lower sides of the planetary wheel 20, so that when the planetary wheel 20 rotates, the planetary wheel gaskets on the upper and lower sides will not move with the rotation of the planetary wheel, so that no wear will occur between the planetary wheel gaskets on the upper and lower sides of the planetary wheel and the planetary carrier.

[0052] In an optional implementation of this embodiment, if Figure 6 and Figure 7 As shown, each planetary wheel gasket 50 designed in the present scheme is provided with a first through hole 5110, and the first through hole 5110 corresponds to the planetary shaft hole 410 of the planetary carrier, so that the planetary shaft 210 of the planetary wheel 20 can pass through the first through hole 5110 and be arranged in the planetary shaft hole 410 of the planetary carrier 40, thereby the planetary wheel 20 can be rotatably fixed to the planetary carrier 40 through the planetary shaft 210.

[0053] As a possible implementation, Figure 7 As shown, the planet carrier 40 of the present embodiment also includes a first oil hole 430 and a second oil hole 440, which are symmetrically distributed on both sides of the planet shaft hole 410, and the first oil hole 430 and the second oil hole 440 are used for the transmission oil to flow out to lubricate the meshing position of the planetary gear 20 and the sun gear 10.

[0054] Based on the planet carrier 40 designed above, Figure 6 As shown, each planetary gear gasket 50 designed in the present scheme is also provided with a second through hole 5120 and a third through hole 5130, wherein the second through hole 5120 corresponds to the first oil hole 430, and the third through hole 5130 corresponds to the second oil hole 440, so that the planetary gear gasket 50 will not block the lubrication oil path at the meshing position of the planetary gear 20 and the sun gear 10, thereby reducing the wear between the planetary gear 20 and the sun gear 10 and improving the working reliability of the planetary gear 20 and the sun gear 10.

[0055] As a possible implementation, Figure 6 and Figure 7As shown, the first through hole 5110 designed in this scheme may include a first circular hole 51110 and a first slot 51120 and a second slot 51130 connected to the first circular hole 51110, the first slot 51120 and the second slot 51130 are symmetrically arranged, and the aperture of the first circular hole 51110 is the same as that of the planetary shaft hole 410; the first slot 51120 and the second slot 51130 are used for the transmission oil to flow out to lubricate the meshing position of the planetary gear 20 and the sun gear 10.

[0056] In the above-mentioned implementation mode, the first through hole 5110 designed in this scheme can not only fix the planetary shaft through the first circular hole 51110, but also let the transmission oil flow out through the first slot hole 51120 and the second slot hole 51130 connected to the first circular hole 51110, so that the planetary gear gasket 50 will not block the lubrication of the meshing position of the planetary gear 20 and the sun gear 10, thereby reducing the wear between the planetary gear 20 and the sun gear 10 and improving the reliability of the operation of the planetary gear 20 and the sun gear 10.

[0057] As a specific implementation method, Figure 6 As shown, the planetary wheel gasket 50 designed in this solution can be a diamond-shaped gasket, and the special-shaped groove 420 can be a diamond-shaped groove, so that the diamond-shaped gasket can be clamped in the diamond-shaped groove by cooperating with the diamond-shaped groove. Of course, the gasket and the special-shaped groove designed in this solution can also be other shapes, not limited to diamonds, for example, pentagons, polygons, etc.

[0058] In an optional implementation of this embodiment, if Figure 8 As shown, the first end 2110 of the planetary shaft 210 designed in this solution can be semi-cylindrical, such as Fig. 9 As shown, the planet carrier 40 further includes a fixing protrusion 450 , the first end of the planet shaft 210 faces the center of the planet carrier 40 , and the first end 2110 of the planet shaft 210 is fixedly matched with the fixing protrusion 450 to achieve radial limiting fixation of the planet shaft 210 .

[0059] In the above embodiment, the orientation of the planetary shaft semi-cylinder can be changed by rotating the planetary shaft 210. After the planetary shaft 210 is installed, the planetary shaft 210 is rotated so that the semi-cylinder at the first end of the planetary shaft faces the center of the planetary carrier 40. In this way, the planetary shaft semi-cylinder cooperates with the fixed protrusion 450 of the planetary carrier 40 to limit the axial movement of the planetary shaft 210 and fix the planetary shaft 210 axially. During installation, the planetary shaft 210 is rotated so that the planetary shaft semi-cylinder faces the outside of the planetary carrier 40, so that the fixed protrusion 450 does not limit the planetary shaft 210, and the planetary shaft 210 can move freely axially.

[0060] In the above-mentioned implementation mode, the first end of the planetary shaft of the planetary gear array of this scheme is designed to be a semi-cylindrical structure, which cooperates with the fixed protrusion 450 of the planetary frame to realize the radial limitation of the planetary shaft, so that the planetary shaft does not need to be fixed by additional devices (such as cylindrical pins, etc.), making the planetary shaft of this scheme easy to install and reducing the components of the planetary gear system, saving costs.

[0061] In an optional implementation of this embodiment, if Fig.10 As shown, the planetary gear system designed in this scheme also includes a planet carrier cover 60, and a planet shaft oil passage 2120 is opened in the planet shaft 210. The planet carrier cover 60 is used to block the transmission oil flowing out of the sun gear oil passage, so that the transmission oil passes through the blockage and enters the planet shaft oil passage and then flows to the meshing position of the planetary gear and the ring gear to achieve gear lubrication.

[0062] Specifically, the oil circuit arrangement of the planetary gear system designed in this scheme can be explained as follows:

[0063] Please refer to Fig.11 The transmission enters through the first oil passage a of the transmission input shaft, then enters the second oil passage b of the transmission input shaft, then enters the inner hub oil passage c of the clutch A, and then enters the sun gear oil passage d. After that, the transmission oil will be blocked by the planetary carrier cover 60. The transmission oil blocked by the planetary carrier cover 60 enters along Figure 8 The planetary shaft oil passage 2120 shown lubricates and cools the needle bearing 80. After passing through the needle bearing, the oil flows out from both sides of the planetary gear to the meshing position of the planetary gear and the gear ring to lubricate the gear.

[0064] Another part of the transmission oil not blocked by the planetary carrier cover 60 flows out through the first oil hole 430 and the second oil hole 440 of the planetary carrier 40, and passes through the first through hole 5110, the second through hole 5120 and the third through hole 5130 of the planetary gear gasket 50 to lubricate the meshing position of the planetary gear 20 and the sun gear 10.

[0065] The present application also provides a dual clutch, the dual clutch is as follows Fig.12 As shown, it includes a planetary gear system of any optional embodiment described above.

[0066] The working principle of the dual clutch is consistent with the principle of realizing dual clutch in conventional planetary gear system, which can be specifically described as follows:

[0067] The dual clutch designed in this scheme includes a first clutch A and a second clutch B. The first clutch driving piston A2 and the first clutch supporting piston A1 form a sealed oil pressure piston chamber. When the hydraulic oil with sufficient oil pressure passes through the oil passage to the piston chamber, it will push the first clutch driving piston A2 to overcome the spring force of the return spring to compress it. The first clutch driving piston A2 pushes the steel plate of the first clutch, so that the first clutch steel plate A3 and the first clutch friction plate A4 fit together to transmit torque. Since the first clutch steel plate A3 is fixedly connected to the first clutch inner hub body A5 through splines, and the first clutch inner hub body A5 is fixedly connected to the sun gear 10 through splines, and the first clutch friction plate A4 is splined to the first clutch outer hub A6, the sun gear 10 and the first clutch outer hub A6 can have the same speed and torque, realizing the function of the first clutch. When the oil pressure is eliminated, the return spring will push the first clutch driving piston A2 back to its original position, so that the first clutch steel plate A3 and the first clutch friction plate A4 are separated, and the sun gear 10 and the first clutch outer hub A6 can rotate freely again.

[0068] The second clutch driving piston B1 and the second clutch supporting piston B2 form a sealed oil pressure piston chamber. When the hydraulic oil with sufficient oil pressure flows to the piston chamber through the oil passage, the second clutch driving piston B1 will be pushed to overcome the spring force of the return spring to compress it. The second clutch driving piston B1 pushes the second clutch steel plate B3, so that the second clutch friction plate B4 and the second clutch steel plate B3 fit together to transmit torque. Since the second clutch steel plate B3 is fixedly connected to the second clutch inner hub body B5 through splines, and the second clutch inner hub body B5 is fixedly connected to the transmission input shaft 70 through splines, and the second clutch friction plate B4 is splined to the second clutch outer hub B6, the transmission input shaft 70 and the second clutch outer hub B6 can have the same speed and torque, realizing the function of the second clutch. When the oil pressure is eliminated, the return spring will push the second clutch driving piston B1 back to its original position, so that the second clutch friction plate B4 and the second clutch steel plate B3 are separated, and the transmission input shaft 70 and the second clutch outer hub B6 can rotate freely again.

[0069] The dual clutch designed as above includes the planetary gear system described above. Therefore, the designed dual clutch can open a special-shaped groove on the planetary carrier and clamp the planetary wheel gasket in the special-shaped groove. In this way, when the planetary wheel rotates, the planetary wheel gasket will not move with the rotation of the planetary wheel, so that no wear will occur between the planetary wheel gasket and the planetary carrier. In this way, the planetary carrier can be made of lightweight materials, thereby reducing the cost and weight of the planetary carrier, and further reducing the cost and weight of the dual clutch.

[0070] The above description is only the preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A planetary gear system, characterized in that: The planetary gear system includes a sun gear, a planet gear, a ring gear, a planet carrier and a planet gear washer; A special-shaped groove is formed at the planet shaft hole of the planet carrier, the planet wheel gasket is clamped in the special-shaped groove, the planet shaft of the planet wheel passes through the planet wheel gasket and is arranged in the planet shaft hole of the planet carrier, so that the planet wheel can be rotatably fixed on the planet carrier, and the planet wheel gasket is used to remain stationary when the planet wheel rotates; The sun gear is used to drive the planet carrier to move when the sun gear rotates. The planet carrier is used to drive the planetary gear to rotate when the planet carrier moves. The planetary gear is used to drive the ring gear to rotate when the planetary gear rotates itself, so as to output the transmission force through the ring gear.

2. The planetary gear system according to claim 1, characterized in that: The special-shaped grooves include a first special-shaped groove and a second special-shaped groove; The planetary gear gasket includes a first gasket and a second gasket, the first gasket is clamped in the first special-shaped groove, the second gasket is clamped in the second special-shaped groove, and the planetary gear is arranged between the first gasket and the second gasket.

3. The planetary gear system according to claim 2, characterized in that: Each gasket is provided with a first through hole; the first through hole corresponds to the planet shaft hole of the planet carrier; The planet shaft of the planetary wheel passes through the first through hole and is arranged in the planet shaft hole of the planetary carrier, so that the planetary wheel can be rotatably fixed on the planetary carrier.

4. The planetary gear system according to claim 3, characterized in that: The planet carrier also includes a first oil hole and a second oil hole; The first oil hole and the second oil hole are symmetrically distributed on both sides of the planetary shaft hole. Each gasket is provided with a second through hole and a third through hole. The second through hole corresponds to the first oil hole, and the third through hole corresponds to the second oil hole.

5. The planetary gear system according to claim 3, characterized in that: The first through hole includes a first circular hole and a first slotted hole and a second slotted hole connected to the first circular hole; The first slotted hole and the second slotted hole are symmetrically arranged, and the aperture of the first circular hole is the same as that of the planetary shaft hole; The first slot hole and the second slot hole are used for transmission oil to flow out to lubricate the meshing positions of the planetary gear and the sun gear.

6. The planetary gear system according to claim 1, characterized in that: The special-shaped groove is a diamond-shaped groove, and the planetary wheel gasket is a diamond-shaped gasket.

7. The planetary gear system according to claim 1, characterized in that: The first end of the planet shaft is semi-cylindrical, and the planet carrier includes a fixed protrusion; The first end of the planet shaft faces the center of the planet carrier, and the first end of the planet shaft is matched and fixed with the fixing protrusion to achieve radial limiting fixation of the planet shaft.

8. The planetary gear system according to claim 1, characterized in that: The planetary gear system further comprises a planet carrier cover, and a planet shaft oil passage is provided in the planet shaft; The planet carrier cover is used to block the transmission oil flowing out of the sun gear oil passage, so that the transmission oil passes through the blockage and enters the planet shaft oil passage and then flows to the meshing position of the planet gear and the ring gear to achieve gear lubrication.

9. The planetary gear system according to claim 1, characterized in that: The planet carrier is made of cast aluminum material.

10. A dual clutch, characterized in that: The dual clutch comprises a planetary gear system according to any one of claims 1-9.

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