Gear assembly

Abstract

The utility model discloses a gear assembly which comprises a driving wheel and a driven wheel set which are in meshing transmission with each other, the driving wheel is arranged on a driving shaft, and the driven wheel set comprises a main gear and an auxiliary gear which are arranged on a driven shaft side by side. The driving shaft and the driven shaft are parallel to each other, and the main gear and the auxiliary gear are engaged with the driving wheel; the main gear and the auxiliary gear can relatively rotate around the axis of the driven shaft; a hydraulic cavity extending in the circumferential direction of the side wall is formed in one of the two opposite side walls of the main gear and the auxiliary gear, and a sliding part matched with the hydraulic cavity is arranged on the other side wall. Wherein the end part of the sliding part is movably inserted into the hydraulic cavity, the hydraulic cavity is divided into a first chamber and a second chamber which are sealed with each other, and pressure difference exists between the first chamber and the second chamber. The gear assembly is simple in structure and easy to mount, and the mounting cost of a hydraulically adjusted anti-backlash gear in the prior art is greatly reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of gear transmission, in particular to a gear assembly. Background Art

[0002] In many mechanical equipment, such as engines and gearboxes, the rotation speed of the shaft system fluctuates, and bending vibration, torsional vibration, etc. may also occur, resulting in transmission errors in the gear pair transmission, causing knocking and howling problems in the gear pair, which in turn causes excessive noise and vibration in the mechanical equipment, seriously affecting the comfort of passengers. At the same time, it will cause abnormal wear on system components and affect the life of components.

[0003] At present, the commonly used scissor gear pairs have a torsion angle and stiffness of the scissor teeth controlled by torsion springs. A large torsional vibration stiffness will cause whistling during gear transmission, and a small torsional stiffness will cause obvious knocking problems on the gears. If the torsional stiffness is too small, fatigue damage to the torsion spring will occur. In addition, the torsion spring needs to be replaced to adjust the stiffness, which is a complicated process and inefficient. Therefore, it is necessary to propose a hydraulically controlled scissor gear structure with a wider torsional vibration stiffness range, convenient adjustment, and no fatigue strength risk.

[0004] In the prior art, although some anti-backlash gear assemblies adopt hydraulic adjustment solutions, this structure is complex and increases the installation cost. For example, a Chinese patent (publication number CN112032281B) discloses an anti-backlash gear and a gear transmission system, the anti-backlash gear includes a main gear; a sub-gear, which is arranged on the main gear and can rotate relative to the main gear, and the number of teeth and the module of the sub-gear and the main gear are the same; a hydraulic adjustment member, which is arranged between the main gear and the sub-gear, one end of the hydraulic adjustment member is connected to the main gear, and the other end is abutted against the sub-gear, and an oil inlet is arranged on the hydraulic adjustment member, and the oil inlet is used to pass hydraulic oil. The length of the hydraulic adjustment member is retractable, so that the tooth surface of the meshing gear meshing with the anti-backlash gear can abut the tooth surface of the main gear and the tooth surface of the sub-gear respectively. The anti-backlash gear uses hydraulic oil to control the elongation of the hydraulic adjustment member, adjust the tooth misalignment of the sub-gear, and realize that the main gear and the sub-gear are in contact with the meshing gear at the same time, so as to achieve the purpose of eliminating side clearance. In this way, a hydraulic adjustment component is provided in the anti-backlash gear, which has a complex structure and is difficult to install. A one-way valve needs to be provided in the hydraulic adjustment component to ensure that the hydraulic oil does not flow back, which increases the installation cost of the anti-backlash gear.

[0005] Therefore, the anti-backlash gear using hydraulic adjustment in the prior art has the problem of complex structure and difficulty in installation, resulting in high installation cost. Utility Model Content

[0006] The utility model aims to solve the problem that the anti-backlash gear using hydraulic adjustment in the prior art has a complex structure and is difficult to install, resulting in a high installation cost.

[0007] To solve the above technical problems, an embodiment of the utility model discloses a gear assembly, which includes a driving wheel and a driven wheel group that are meshed with each other for transmission, the driving wheel is arranged on a driving shaft, and the driven wheel group includes a main gear and a sub-gear arranged side by side on the driven shaft; the driving shaft and the driven shaft are parallel to each other, and the main gear and the sub-gear are both meshed with the driving wheel; the main gear and the sub-gear can rotate relative to each other around the axis of the driven shaft; a hydraulic cavity extending along its circumference is formed on one of the two side walls opposite to each other of the main gear and the sub-gear, and a sliding portion adapted to the hydraulic cavity is arranged on the other side wall; wherein an end of the sliding portion is movably inserted into the hydraulic cavity to separate the hydraulic cavity into a first chamber and a second chamber that are sealed from each other, and there is a pressure difference between the first chamber and the second chamber.

[0008] By adopting the above technical scheme, when the gear assembly is in use, a driving wheel and a driven wheel group that mesh with each other are arranged for transmission, and the driving wheel is arranged on the driving shaft, and the driven wheel group includes a main gear and a sub-gear arranged side by side on the driven shaft; the driving shaft and the driven shaft are parallel to each other, and the main gear and the sub-gear are both meshed with the driving wheel, so that the power transmission has a constant transmission ratio and high transmission stability; the main gear and the sub-gear can rotate relative to each other around the axis of the driven shaft; a hydraulic cavity extending along its circumferential direction is formed on one of the two side walls of the main gear and the sub-gear that are opposite to each other, and a sliding part adapted to the hydraulic cavity is arranged on the other side wall; and the end of the sliding part is movably inserted into the hydraulic cavity to separate the hydraulic cavity into a first chamber and a second chamber that are sealed from each other, and there is a pressure difference between the first chamber and the second chamber, so that the main gear and the sub-gear in the driven wheel group can form a scissors gear, so that the teeth of the main gear and the sub-gear abut against the transmission teeth of the driving wheel on both sides of the transmission direction, thereby eliminating the gap and damping the driving wheel meshed therewith. Through the above-mentioned structural setting, compared with the existing technology, this gear assembly cleverly sets a hydraulic chamber and a sliding part on the two side walls opposite to each other of the main gear and the auxiliary gear, and the structure of the gear itself can directly cause the main gear and the auxiliary gear to be misaligned, thereby achieving the effect of eliminating backlash and damping in the gear transmission process. On the basis of ensuring high transmission efficiency, the structure can be simplified, and it has the advantages of easy installation and reduced installation cost.

[0009] An embodiment of the utility model also discloses a gear assembly, wherein the hydraulic chamber is configured as a groove formed on one side wall, and the groove extends along the circumference of one side wall and around the axis of the driven shaft; the sliding portion is configured as a protrusion formed on the other side wall, and the protrusion protrudes from the other side wall and extends toward one side wall, and at least the shape of the end portion is adapted to the groove; the end portion of the protrusion is movably inserted into the groove, dividing the groove into a first chamber and a second chamber that are sealed from each other and have variable volumes.

[0010] The above technical solution is adopted, by setting the hydraulic chamber as a groove formed on one side wall, the groove extends along the circumference of one side wall and around the axis of the driven shaft, that is, the groove is formed into an arc structure with the same center as the gear formed thereon; the sliding part is set as a protrusion formed on the other side wall, the protrusion protrudes from the other side wall and extends toward one side wall, and at least the shape of the end is adapted to the groove; so that when the end of the protrusion is inserted into the groove of the arc structure, the protrusion can slide along the extension direction of the groove. By movably inserting the end of the protrusion into the groove, the groove is divided into a first chamber and a second chamber that are sealed from each other and have variable volumes, so that when the gear assembly is in use, hydraulic oil can be injected into the first chamber and the second chamber, and because there is a hydraulic pressure difference between the first chamber and the second chamber, the main gear and the auxiliary gear in the driven wheel group are staggered, and finally the effect of eliminating backlash and damping in the gear transmission process is achieved.

[0011] An embodiment of the utility model also discloses a gear assembly, wherein the groove includes a first recess and a second recess located at two ends, and a guide recess located between the first recess and the second recess, wherein the width of the guide recess is smaller than the width of the first recess and the second recess; and the protrusion is a protrusion extending along the circumference of the other side wall and around the axis of the driven shaft, and the extension length of the protrusion is smaller than the extension length of the groove; wherein the protrusion is adapted in the groove, and the outer wall of the adapting part of the protrusion and the guide recess is sealed and abutted against the inner side wall of the guide recess.

[0012] By adopting the above technical scheme, the groove is divided into a first recess, a second recess and a guide recess, and the width of the guide recess is smaller than the width of the first recess and the second recess. Through this arrangement, the accommodation volume of the first recess and the second recess is increased, and the accommodation volume of the guide recess is reduced. The protrusion is a protrusion extending along the circumference of the other side wall and around the axis of the driven shaft, and the extension length of the protrusion is smaller than the extension length of the groove; and the protrusion is adapted in the groove, and the outer wall of the adapting part of the protrusion and the guide recess is sealed and abutted with the inner side wall of the guide recess. Therefore, since the width of the guide recess is smaller than the width of the first recess and the second recess, the width of the protrusion is also smaller than the width of the first recess and the second recess. Further, when the surface of the protrusion is sealed and abutted with the accommodation space of the guide recess, the contact area between the protrusion and the guide recess can be reduced, thereby reducing the friction between the protrusion and the guide recess, which is more conducive to the adaptation and sliding of the protrusion in the guide recess.

[0013] An embodiment of the utility model also discloses a gear assembly, in which a first oil circuit is formed near a first chamber in one of the two side walls opposite to each other of a main gear and a secondary gear, and a second oil circuit is formed near a second chamber; wherein one end of the first oil circuit is communicated with the first chamber, and the other end extends to the outside of the side wall of the main gear or the secondary gear; one end of the second oil circuit is communicated with the second chamber, and the other end extends to the outside of the side wall of the main gear or the secondary gear.

[0014] By adopting the above technical solution, a first oil circuit and a second oil circuit are arranged in one of the two side walls opposite to each other of the main gear and the auxiliary gear, and one end of the first oil circuit is connected with the first chamber, and the other end extends to the outside of the side wall of the main gear or the auxiliary gear; one end of the second oil circuit is connected with the second chamber, and the other end extends to the outside of the side wall of the main gear or the auxiliary gear. Therefore, during use, it is convenient to infuse hydraulic oil from the outside of the side wall of the main gear or the auxiliary gear to the first chamber and the second chamber via the first oil circuit and the second oil circuit, and by adjusting the hydraulic oil pressure difference between the first chamber and the second chamber, the protrusion is pushed to slide toward the chamber with low pressure, so that the main gear and the auxiliary gear form a scissors gear to eliminate clearance and damp the transmission of the driving wheel.

[0015] An embodiment of the utility model also discloses a gear assembly, wherein a first auxiliary oil circuit is formed at a position on the driven shaft corresponding to the first oil circuit, and a second auxiliary oil circuit is formed at a position corresponding to the second oil circuit; the first auxiliary oil circuit and the second auxiliary oil circuit extend along the length direction of the driven shaft, and oil filling ports are provided at both ends of the driven shaft; wherein, one end of the first auxiliary oil circuit is connected with the other end of the first oil circuit, and one end of the second auxiliary oil circuit is connected with the other end of the second oil circuit, and the other end of the first auxiliary oil circuit and the other end of the second auxiliary oil circuit are respectively connected with the oil filling ports at both ends of the driven shaft.

[0016] By adopting the above technical solution, during use, the hydraulic oil flows into the first oil circuit and the second oil circuit through the first auxiliary oil circuit and the second auxiliary oil circuit on the driven shaft, and then is infused into the first chamber and the second chamber. Such an arrangement improves the integrity of the gear assembly; by extending the first auxiliary oil circuit and the second auxiliary oil circuit along the length direction of the driven shaft, and providing oil filling ports at both ends of the driven shaft, during use, the hydraulic oil can be injected through the oil filling ports at both ends of the driven shaft, and the main gear and the auxiliary gear can be directly injected without disassembling, thereby improving the convenience of personnel when injecting oil; By connecting one end of the first auxiliary oil circuit with the other end of the first oil circuit, connecting one end of the second auxiliary oil circuit with the other end of the second oil circuit, and connecting the other end of the first auxiliary oil circuit and the other end of the second auxiliary oil circuit with the oil filling ports at both ends of the driven shaft respectively, during use, the hydraulic oil can be injected through the oil filling port and then injected into the first oil circuit and the second oil circuit through the first auxiliary oil circuit and the second auxiliary oil circuit, and finally injected into the first chamber and the second chamber. The connecting design of the auxiliary oil circuit of the driven shaft and the main gear or the auxiliary gear oil circuit improves the integrity of the gear assembly and also improves the convenience of the oil filling process.

[0017] An embodiment of the utility model also discloses a gear assembly, wherein the driven shaft also includes an oil port blocking device, the oil port blocking device includes a first oil port blocking device and a second oil port blocking device, and the first oil port blocking device and the second oil port blocking device are respectively detachably connected to the oil filling ports at both ends of the driven shaft.

[0018] By adopting the above technical scheme, a first oil port blocking device and a second oil port blocking device are arranged at the oil filling port of the driven shaft, so that during use, after the hydraulic oil is injected into the oil filling port, the first oil port blocking device and the second oil port blocking device can prevent the hydraulic oil from leaking. The arrangement of the first oil port blocking device enables the first auxiliary oil circuit, the first oil circuit and the first chamber to form a sealed space; the arrangement of the second oil port blocking device enables the second auxiliary oil circuit, the second oil circuit and the second chamber to form a sealed space, and the volume of the sealed space is changed by adjusting the depth of the first oil port blocking device and the second oil port blocking device inserted into the oil filling ports on both sides of the driven shaft, thereby controlling the hydraulic oil pressure difference between the first chamber and the second chamber, thereby improving the convenience of controlling the hydraulic oil pressure difference between the first chamber and the second chamber; by detachably connecting the first oil port blocking device and the second oil port blocking device to the oil filling ports at both ends of the driven shaft, it is convenient to disassemble when replacing the hydraulic oil during use.

[0019] The embodiment of the utility model further discloses a gear assembly, wherein the first oil port blocking device and the second oil port blocking device are respectively threadedly connected to the oil filling ports at both ends of the driven shaft.

[0020] By adopting the above technical solution, the first oil port blocking device and the second oil port blocking device are respectively set to the oil filling ports at both ends of the driven shaft as threaded connections, and the threaded connection has the advantages of simple structure, reliable connection and easy disassembly. Therefore, the threaded connection is applied to the gear assembly, so that during use, the hydraulic oil in the oil circuit is sealed safely and reliably, and it is easy to disassemble when replacing the hydraulic oil.

[0021] The embodiment of the utility model further discloses a gear assembly, wherein the first oil port blocking device and the second oil port blocking device are configured as sealing plugs.

[0022] By adopting the above technical solution, the production cost of the gear assembly is reduced by setting the first oil port blocking device and the second oil port blocking device as sealing plugs, and the gear assembly can be used multiple times to save resources. In addition, the gear assembly has the characteristics of easy disassembly and assembly and good sealing performance.

[0023] The embodiment of the utility model also discloses a gear assembly, wherein two opposite side walls of the main gear and the auxiliary gear fit each other; and the gear assembly further comprises a sealing rubber ring, which is arranged in the hydraulic cavity and matches with the inner circumferential wall of the hydraulic cavity.

[0024] By adopting the above technical solution, the two side walls of the main gear and the auxiliary gear facing each other are fitted together, so that the first recess, the second recess and the guide recess cooperate with the protrusion and the side wall to which the protrusion belongs to form the first chamber and the second chamber. During use, the hydraulic oil is injected into the first chamber and the second chamber, which improves the sealing of the hydraulic oil in the chamber; by arranging a sealing rubber ring in the hydraulic chamber that matches the inner peripheral wall of the hydraulic chamber, the direct connection between the protrusion and the hydraulic chamber is avoided, thereby causing wear of the protrusion and the hydraulic chamber. During use, the worn sealing rubber ring can be regularly replaced to improve the sealing of the hydraulic chamber. Therefore, the setting of the sealing rubber ring not only reduces the installation cost of the gear assembly, but also improves the sealing of the hydraulic chamber.

[0025] The embodiment of the utility model further discloses a gear assembly, wherein one of the main gear and the auxiliary gear is rotatably connected to the driven shaft, and the other is rigidly connected to the driven shaft.

[0026] By adopting the above technical solution, during use, one of the main gear and the auxiliary gear is rotatably connected to the driven shaft and the other is rigidly connected to the driven shaft, so that the rigidly connected gear can transmit the power transmitted by the driving wheel, and the rotatably connected gear can form a scissors gear with the rigidly connected gear through hydraulic adjustment, thereby eliminating backlash and reducing shock when the driving wheel is transmitting.

[0027] The beneficial effects of the utility model are:

[0028] The utility model discloses a gear assembly, which includes a driving wheel and a driven wheel group that mesh with each other for transmission, the driving wheel is arranged on the driving shaft, and the driven wheel group includes a main gear and a sub-gear arranged side by side on the driven shaft; the driving shaft and the driven shaft are parallel to each other, and the main gear and the sub-gear are meshed with the driving wheel; the main gear and the sub-gear can rotate relative to each other around the axis of the driven shaft; a hydraulic cavity extending along its circumference is formed on one of the two side walls opposite to each other of the main gear and the sub-gear, and a sliding part adapted to the hydraulic cavity is arranged on the other side wall; wherein the end of the sliding part is movably inserted into the hydraulic cavity, and the hydraulic cavity is divided into a first chamber and a second chamber sealed from each other, and there is a pressure difference between the first chamber and the second chamber. The gear assembly cleverly arranges the hydraulic cavity and the sliding part on the side walls opposite to the main gear and the sub-gear, so as to achieve the effect of eliminating backlash and damping in the gear transmission process, has the advantages of simple structure and easy installation, and greatly reduces the installation cost of the anti-backlash gear of hydraulic adjustment in the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 A schematic diagram of the three-dimensional structure of a gear assembly provided in an embodiment of the utility model;

[0030] Figure 2A schematic diagram of the exploded structure of a driven wheel assembly provided in an embodiment of the utility model;

[0031] Figure 3 A schematic diagram of the three-dimensional structure of the main gear provided in an embodiment of the utility model;

[0032] Figure 4 A schematic diagram of the three-dimensional structure of a secondary gear provided in an embodiment of the utility model;

[0033] Figure 5 A schematic diagram of the three-dimensional structure of the main gear and the auxiliary gear provided by the embodiment of the utility model after the two side walls thereof are fitted together;

[0034] Figure 6 A schematic diagram of the three-dimensional structure of a driven shaft provided in an embodiment of the utility model;

[0035] Figure 7 A schematic diagram of the three-dimensional structure of a sealing rubber ring provided in an embodiment of the utility model;

[0036] Figure 8 A schematic diagram of the three-dimensional structure of the sealing plug provided in an embodiment of the utility model;

[0037] Fig. 9 A schematic structural diagram of a thrust plate provided in an embodiment of the utility model.

[0038] Description of reference numerals:

[0039] 10. Gear assembly;

[0040] 100. Driving wheel;

[0041] 110. Driving shaft;

[0042] 120, driven wheel set;

[0043] 121, main gear;

[0044] 1210, hydraulic chamber; 1211, first oil circuit; 1212, second oil circuit;

[0045] 122, auxiliary gear;

[0046] 1220, sliding part;

[0047] 123, driven shaft;

[0048] 1230, first auxiliary oil circuit; 1231, second auxiliary oil circuit; 1232, oil filling port;

[0049] 124. First oil port blocking device;

[0050] 125. Second oil port blocking device;

[0051] 126. Thrust plate;

[0052] 127. Sealing rubber ring;

[0053] 1270. Guide recess; 1271. First oil hole; 1272. Second oil hole; 1273. First recess; 1274. Second recess;

[0054] 128, first chamber;

[0055] 129, second chamber;

[0056] H, the width of the guide recess;

[0057] h1, the width of the first recess;

[0058] h2, the width of the second recess. DETAILED DESCRIPTION

[0059] In the existing gear transmission, in theory, a pair of gears should have no side clearance when meshing, but in fact, in order to compensate for the dimensional changes caused by processing, installation errors and temperature changes to prevent them from getting stuck, a certain amount of side clearance must be left on the non-working surface of the gear. Gear transmission mechanisms all have side clearances, which are used to prevent the gears from getting stuck due to errors and thermal deformation, and to leave space for the lubricating oil film between the tooth surfaces. However, the side clearance also brings idle travel to the mechanism during reversal, making it impossible for the mechanism to be accurately positioned. Therefore, in order to reduce or eliminate the adverse effects of the side clearance on the mechanism, an anti-backlash system is required. Common anti-backlash mechanisms include: mechanical anti-backlash, spring anti-backlash, etc.

[0060] In the prior art, the anti-backlash gear adjusted by hydraulic pressure has the problem of complex structure and difficult installation, resulting in high installation cost.

[0061] To solve this problem, the embodiment of the utility model discloses a gear assembly, which includes a driving wheel and a driven wheel group that mesh with each other, the driving wheel is arranged on the driving shaft, and the driven wheel group includes a main gear and a sub-gear arranged side by side on the driven shaft; the driving shaft and the driven shaft are parallel to each other, and the main gear and the sub-gear are meshed with the driving wheel; the main gear and the sub-gear can rotate relative to each other around the axis of the driven shaft; a hydraulic cavity extending along its circumferential direction is formed on one of the two side walls of the main gear and the sub-gear, and a sliding part adapted to the hydraulic cavity is arranged on the other side wall; wherein the end of the sliding part is movably inserted into the hydraulic cavity, and the hydraulic cavity is divided into a first chamber and a second chamber that are sealed from each other, and there is a pressure difference between the first chamber and the second chamber. This gear assembly has a simple structure and is easy to install, which greatly reduces the installation cost of the anti-backlash gear of hydraulic adjustment in the prior art.

[0062] In order to make the purpose, technical solution and advantages of the present invention more clear, the implementation mode of the present invention will be further described in detail below with reference to the accompanying drawings.

[0063] like Figure 1 and Figure 2 As shown, the embodiment of the utility model discloses a gear assembly 10, which includes a driving wheel 100 and a driven wheel set 120 that mesh with each other, the driving wheel 100 is arranged on the driving shaft 110, and the driven wheel set 120 includes a main gear 121 and a sub-gear 122 that are arranged side by side on the driven shaft 123; the driving shaft 110 and the driven shaft 123 are parallel to each other, and the main gear 121 and the sub-gear 122 are both meshed with the driving wheel 100; the main gear 121 and the sub-gear 122 can rotate relative to each other around the axis of the driven shaft 123. It should be noted that, with respect to the model and specification of the gear, those skilled in the art can design it according to actual conditions and specific needs, and this embodiment does not specifically limit this.

[0064] Specifically, in this embodiment, a hydraulic cavity 1210 extending along the circumferential direction of the main gear 121 and the auxiliary gear 122 is formed on the side wall opposite to each other, and a sliding portion 1220 adapted to the hydraulic cavity 1210 is provided on the side wall opposite to the auxiliary gear 122 and the main gear 121; wherein the end of the sliding portion 1220 is movably inserted into the hydraulic cavity 1210, and the hydraulic cavity 1210 is separated into a first chamber 128 and a second chamber 129 sealed from each other, and there is a pressure difference between the first chamber 128 and the second chamber 129. It should be noted that the shape of the hydraulic cavity 1210 is an arc extending along the circumferential direction of the main gear 121.

[0065] More specifically, in one embodiment, a hydraulic cavity 1210 extending along the circumference thereof is formed on the side wall opposite to the secondary gear 122 and the main gear 121, and a sliding portion 1220 adapted to the hydraulic cavity 1210 is provided on the side wall opposite to the main gear 121 and the secondary gear 122; wherein, the end of the sliding portion 1220 is movably inserted into the hydraulic cavity 1210, dividing the hydraulic cavity 1210 into a first chamber 128 and a second chamber 129 which are sealed from each other, and there is a pressure difference between the first chamber 128 and the second chamber 129.

[0066] It should be understood that, in the present embodiment, the pressure difference between the first chamber 128 and the second chamber 129 is the pressure difference between the hydraulic oil and the sliding part 1220, and the pressure difference between the hydraulic oil in the first chamber 128 and the second chamber 129 and the sliding part 1220 is proportional to the preload force F of the meshing teeth of the main gear 121 and the secondary gear 122 on the transmission teeth of the driving wheel 100. When the pressure is subjected to a certain force area, the greater the pressure, the greater the pressure. In the present utility model, since the sliding part 1220 divides the hydraulic chamber 1210 into the first chamber 128 and the second chamber 129, after the hydraulic oil is injected into the two chambers, the force areas of the hydraulic oil in the two chambers on both sides of the sliding part 1220 are equal, so the chamber with a stronger hydraulic oil pressure exerts a greater pressure on the sliding part 1220. It should be noted that the pressure of the hydraulic oil in the first chamber 128 on the sliding part 1220 may be greater than the pressure of the hydraulic oil in the second chamber 129 on the sliding part 1220. Of course, the pressure of the hydraulic oil in the second chamber 129 on the sliding part 1220 may also be greater than the pressure of the hydraulic oil in the first chamber 128 on the sliding part 1220. The specific setting can be designed by technicians in this field according to actual conditions and specific needs, and this embodiment does not make any specific limitations on this.

[0067] Specifically, in the present embodiment, the pressure difference between the hydraulic oil in the first chamber 128 and the second chamber 129 and the sliding part 1220 can be set to any pressure difference between 20N and 100N, for example, it can be 20N, 40N, 70N, 100N, etc. The specific setting of the pressure difference between the hydraulic oil in the first chamber 128 and the second chamber 129 and the sliding part 1220 can be designed by those skilled in the art according to actual conditions and specific needs, and this embodiment does not make any specific limitations on this.

[0068] It should be understood that, in one embodiment, the pressure difference between the first chamber 128 and the second chamber 129 may also be a pressure difference, and when the volume of the first chamber 128 and the second chamber 129 remains unchanged, the pressure difference of the hydraulic oil therein is proportional to the preload force F of the meshing teeth of the main gear 121 and the secondary gear 122 on the transmission teeth of the driving wheel 100. As for the pressure, when the force area is constant, the greater the pressure, the greater the pressure. It should be noted that the pressure of the hydraulic oil in the first chamber 128 may be greater than the pressure of the hydraulic oil in the second chamber 129. Of course, the pressure of the hydraulic oil in the second chamber 129 may also be greater than the pressure of the hydraulic oil in the first chamber 128. The specific setting can be designed by those skilled in the art according to actual conditions and specific needs, and this embodiment does not make specific limitations on this.

[0069] Specifically, in one embodiment, the pressure difference of the hydraulic oil in the first chamber 128 and the second chamber 129 can be set to any pressure difference between 20Pa and 100Pa, for example, it can be 20Pa, 40Pa, 70Pa, 100Pa, etc. The specific setting of the pressure difference of the hydraulic oil in the first chamber 128 and the second chamber 129 can be designed by technical personnel in this field according to actual conditions and specific needs, and this embodiment does not make any specific limitations on this.

[0070] Furthermore, the embodiment of the present utility model also discloses a gear assembly 10, such as Figures 3 to 5 As shown, the hydraulic chamber 1210 is configured as a groove formed on one side wall, the groove extends along the circumference of one side wall and around the axis of the driven shaft 123; the sliding portion 1220 is configured as a protrusion formed on the other side wall, the protrusion protrudes from the other side wall and extends toward one side wall.

[0071] Specifically, in this embodiment, the two opposite sides of the main gear 121 and the auxiliary gear 122 fit each other, and the protrusion is movably inserted into the groove, dividing the groove into a first chamber 128 and a second chamber 129 that are sealed and have variable volumes. It should be noted that at this time, since a side wall of the main gear 121 with the groove fits with a side wall of the auxiliary gear 122 with the protrusion, the groove forms a first chamber 128 and a second chamber 129 that are sealed and have variable volumes.

[0072] More specifically, in one embodiment, the shape of the end of the projection is adapted to the groove, and when the end of the projection is movably inserted into the groove, the side wall of the end of the projection forms a structure that can seal the groove, so that the groove is divided into a first chamber 128 and a second chamber 129 that are sealed to each other and have variable volumes. It should be noted that at this time, since the structure of the end of the projection cooperates with the groove to form a sealed first chamber 128 and a second chamber 129 with variable volumes, the two side walls of the main gear 121 and the auxiliary gear 122 do not need to fit each other. Regarding the structural shape of the sealing groove at the end of the projection, it can be set to an arc, a quadrilateral, a circle, etc., and those skilled in the art can design it according to actual conditions and specific needs without affecting the sealing of the groove, and this embodiment does not make specific limitations on this.

[0073] Furthermore, the embodiment of the present utility model also discloses a gear assembly 10, such as Figure 3 and Figure 6As shown, the sliding portion 1220 is directly set as a groove, and a sealing rubber ring 127 that is interference fit with the groove is set in the groove. The sealing rubber ring 127 has a first recess 1273 and a second recess 1274, and a guide recess 1270 located between the first recess 1273 and the second recess 1274. The width H of the guide recess 1270 is smaller than the width h1 of the first recess 1273 and the width h2 of the second recess 1274; and the protrusion is a protrusion extending along the circumference of the other side wall and around the axis of the driven shaft 123, and the extension length of the protrusion is smaller than the extension length of the groove; wherein the protrusion is interference fit with the guide recess 1270 on the sealing rubber ring 127, and two independent first chambers 128 and second chambers 129 are formed at both ends of the groove. It should be noted that, in this solution, the width h1 of the first recess 1273 and the width h2 of the second recess 1274 are preferably equal, the width H of the guide recess 1270 is smaller than the width h1 of the first recess 1273 and the width h2 of the second recess 1274, and the width H of the guide recess 1270 can be set to any width between 1 / 2 and 1 / 5 times the width h1 of the first recess 1273 and the width h2 of the second recess 1274, for example, the width H of the guide recess 1270 is 1 / 2, 1 / 3, 1 / 4, 1 / 5, etc. times the width h1 of the first recess 1273 and the width h2 of the second recess 1274. The specific width H of the guide recess 1270 and the multiples of the width h1 of the first recess 1273 and the width h2 of the second recess 1274 can be designed by those skilled in the art according to actual conditions and specific needs, and this embodiment does not make any specific limitation on this.

[0074] Specifically, in one embodiment, the sliding portion 1220 is configured as a groove having a first recess 1273 and a second recess 1274 at both ends, and a guide recess 1270 located between the first recess 1273 and the second recess 1274, the radial width of the guide recess 1270 along the driven wheel group 120 is smaller than the radial width of the driven wheel group 120 of the first recess 1273 and the second recess 1274; and the protrusion is a protrusion extending along the circumference of the other side wall and around the axis of the driven shaft 123, and the extension length of the protrusion is smaller than the extension length of the groove; wherein the protrusion is adapted in the groove, and the outer wall of the adapting part of the protrusion and the guide recess 1270 is sealed and abutted against the inner wall of the guide recess 1270. It should be noted that the angle between the two end vertices of the groove and the center of the gear can be set to 30°~90°, and can be specifically set to any angle between 30°~90°, for example, it can be 30°, 45°, 70°, 90°, etc. The specific angle setting between the end vertex of the groove and the center of the gear can be designed by technical personnel in this field according to actual conditions and specific needs, and this embodiment does not make any specific limitations on this.

[0075] Furthermore, the embodiment of the present utility model also discloses a gear assembly 10, such as Figure 3 As shown, in one of the two side walls of the main gear 121 and the auxiliary gear 122 facing each other, a first oil passage 1211 is formed near the first chamber 128, and a second oil passage 1212 is formed near the second chamber 129; wherein one end of the first oil passage 1211 is connected to the first chamber 128, and the other end extends to the outside of the side wall of the main gear 121 or the auxiliary gear 122; one end of the second oil passage 1212 is connected to the second chamber 129, and the other end extends to the outside of the side wall of the main gear 121 or the auxiliary gear 122. Of course, the shape of the first oil passage 1211 and the second oil passage 1212 in the side wall of the main gear 121 or the auxiliary gear 122 can be designed by those skilled in the art according to actual conditions and specific needs, and this embodiment does not specifically limit this.

[0076] Specifically, in the present embodiment, a first oil passage 1211 is formed near the first chamber 128 on the main gear 121, and a second oil passage 1212 is formed near the second chamber 129, and one end of the first oil passage 1211 is communicated with the first chamber 128, and the other end extends to the outside of the side wall of the main gear 121; one end of the second oil passage 1212 is communicated with the second chamber 129, and the other end extends to the outside of the side wall of the main gear 121. Therefore, during use, it is convenient for hydraulic oil to be injected from the outside of the side wall of the main gear 121 to the first chamber 128 and the second chamber 129 via the first oil passage 1211 and the second oil passage 1212, so that by adjusting the hydraulic oil pressure difference between the first chamber 128 and the second chamber 129, the protrusion adapted in the guide groove is pushed to slide toward the chamber with low pressure, and finally the main gear 121 and the auxiliary gear 122 form a scissors gear to eliminate backlash and damp the transmission of the driving wheel 100.

[0077] More specifically, in another embodiment, a first oil circuit 1211 is formed on the sub-gear 122 near the first chamber 128, and a second oil circuit 1212 is formed near the second chamber 129. The arrangement of the oil circuit and the chamber and the arrangement method of the oil circuit in the gear are the same as those in the above-mentioned embodiment.

[0078] Furthermore, the embodiment of the present utility model also discloses a gear assembly 10, such as Figure 7As shown, a first auxiliary oil circuit 1230 is formed at a position corresponding to the first oil circuit 1211 on the driven shaft 123, and a second auxiliary oil circuit 1231 is formed at a position corresponding to the second oil circuit 1212; the first auxiliary oil circuit 1230 and the second auxiliary oil circuit 1231 extend along the length direction of the driven shaft 123, and both ends of the driven shaft 123 are provided with oil injection ports 1232; wherein, one end of the first auxiliary oil circuit 1230 is connected to the other end of the first oil circuit 1211, one end of the second auxiliary oil circuit 1231 is connected to the other end of the second oil circuit 1212, and the other end of the first auxiliary oil circuit 1230 and the other end of the second auxiliary oil circuit 1231 are respectively connected to the oil injection ports 1232 at both ends of the driven shaft 123. Of course, the shape of the first auxiliary oil circuit 1230 and the second auxiliary oil circuit 1231 in the driven shaft 123 can be designed by those skilled in the art according to actual conditions and specific needs, and this embodiment does not specifically limit this.

[0079] Specifically, a first auxiliary oil circuit 1230 is formed at a position corresponding to the first oil circuit 1211 on the driven shaft 123, and a second auxiliary oil circuit 1231 is formed at a position corresponding to the second oil circuit 1212, so that during use, the hydraulic oil flows into the first oil circuit 1211 and the second oil circuit 1212 via the first auxiliary oil circuit 1230 and the second auxiliary oil circuit 1231 on the driven shaft 123, and then is injected into the first chamber 128 and the second chamber 129. Such an arrangement improves the integrity of the gear assembly 10; the first auxiliary oil circuit 1230 and the second auxiliary oil circuit 1231 are extended along the length direction of the driven shaft 123, and oil injection ports 1232 are provided at both ends of the driven shaft 123, so that during use, the hydraulic oil can be injected through the oil injection ports 1232 at both ends of the driven shaft 123, without the need to perform oil injection on the main gear 121 and the secondary gear 122. The gear assembly 120 has two oil circuits 1230 and 1231 which are connected to each other via the oil filling ports 1232. The oil filling ports 1232 are connected to the second gear 1202 and the second gear 1203 are connected to the second gear 1204. The gear assembly 120 has two oil circuits 1230 and 1231 which are connected to each other via the oil filling ports 1232. The oil filling ports 1232 are connected to the second gear 1202 and the second gear 1203 are connected to the second gear 1204. It should be noted that the port shape of the oil filling port 1232 can be circular, quadrilateral, hexagonal, octagonal, etc. Regarding the port shape setting of the oil filling port 1232, technical personnel in this field can design it according to actual conditions and specific needs, and this embodiment does not make any specific limitations on this.

[0080] Furthermore, the embodiment of the present utility model also discloses a gear assembly 10, such as Figure 8 As shown, the driven shaft 123 also includes an oil port blocking device, which includes a first oil port blocking device 124 and a second oil port blocking device 125. The first oil port blocking device 124 and the second oil port blocking device 125 are respectively detachably connected to the oil filling ports 1232 at both ends of the driven shaft 123.

[0081] Specifically, by setting the first oil port blocking device 124 and the second oil port blocking device 125 at the oil filling port 1232 of the driven shaft 123, during use, after the hydraulic oil is injected into the oil filling port 1232, the first oil port blocking device 124 and the second oil port blocking device 125 can prevent the hydraulic oil from leaking out. The setting of the first oil port blocking device 124 enables the first auxiliary oil circuit 1230, the first oil circuit 1211 and the first chamber 128 to form a sealed space; the setting of the second oil port blocking device 125 enables the second auxiliary oil circuit 1231, the second oil circuit 1212 and the first chamber 128 to form a sealed space. The two chambers 129 form a sealed space, and the volume of the first oil port blocking device 124 and the second oil port blocking device 125 inserted into the oil filling ports 1232 on both sides of the driven shaft 123 is adjusted to control the hydraulic oil pressure difference between the first chamber 128 and the second chamber 129, thereby improving the convenience of controlling the hydraulic oil pressure difference between the first chamber 128 and the second chamber 129; the first oil port blocking device 124 and the second oil port blocking device 125 are detachably connected to the oil filling ports 1232 at both ends of the driven shaft 123, so that it is easy to disassemble when replacing the hydraulic oil during use. It should be noted that the above-mentioned detachable connection can be a snap connection, a screw connection, etc., and those skilled in the art can design it according to actual conditions and specific needs, and this embodiment does not make specific limitations on this.

[0082] Furthermore, the embodiment of the present utility model further discloses a gear assembly 10 , wherein the first oil port blocking device 124 and the second oil port blocking device 125 are respectively threadedly connected to the oil filling ports 1232 at both ends of the driven shaft 123 .

[0083] Specifically, the first oil port blocking device 124 and the second oil port blocking device 125 are respectively provided with the oil filling ports 1232 at both ends of the driven shaft 123 as threaded connections, and the threaded connection has the advantages of simple structure, reliable connection, and convenient disassembly. Therefore, the threaded connection is applied to the gear assembly 10, so that during use, the hydraulic oil in the oil circuit is sealed safely and reliably, and it is easy to disassemble when the hydraulic oil is replaced. It should be noted that the internal thread can be provided on the first oil port blocking device 124 and the second oil port blocking device 125, and can also be provided on the oil filling port 1232, and the external thread can be provided on the oil filling port 1232, and can also be provided on the first oil port blocking device 124 and the second oil port blocking device 125. Those skilled in the art can design according to actual conditions and specific needs, and this embodiment does not make specific limitations on this.

[0084] Furthermore, the embodiment of the present utility model further discloses a gear assembly 10, wherein the first oil port blocking device 124 and the second oil port blocking device 125 are configured as sealing plugs.

[0085] Specifically, by setting the first oil port blocking device 124 and the second oil port blocking device 125 as sealing plugs, the production cost of the gear assembly 10 is reduced, and it can be used multiple times, saving resources. In addition, it is easy to disassemble and has good sealing performance. It should be noted that the sealing plug can be set as a metal sealing plug or a rubber sealing plug. Those skilled in the art can design it according to actual conditions and specific needs, and this embodiment does not make specific limitations on this.

[0086] Furthermore, an embodiment of the present invention also discloses a gear assembly 10, in which two opposite side walls of the main gear 121 and the auxiliary gear 122 are in contact with each other; and the gear assembly 10 also includes a sealing rubber ring 127, which is arranged in the hydraulic cavity 1210 and adapted to the inner circumferential wall of the hydraulic cavity 1210.

[0087] Specifically, in this embodiment, by fitting the two opposite side walls of the main gear 121 and the auxiliary gear 122 together, the first recess 1273 and the second recess 1274 on the sealing rubber ring 127 and the guide recess 1270 cooperate with the protrusion on the auxiliary gear 122 and the side wall of the auxiliary gear 122 to form the first chamber 128 and the second chamber 129. During use, the hydraulic oil is injected into the first chamber 128 and the second chamber 129, thereby improving the sealing of the hydraulic oil in the chamber; by arranging the sealing rubber ring 127 that matches the inner peripheral wall of the hydraulic chamber 1210 in the hydraulic chamber 1210, the protrusion is prevented from being directly connected to the hydraulic chamber 1210, thereby causing wear of the protrusion and the hydraulic chamber 1210. During use, the worn sealing rubber ring 127 can be regularly replaced to improve the sealing of the hydraulic chamber 1210. Therefore, the arrangement of the sealing rubber ring 127 not only reduces the installation cost of the gear assembly 10, but also improves the sealing of the hydraulic chamber 1210.

[0088] More specifically, in one embodiment, a protrusion is provided on the main gear 121, a groove is provided on the sub-gear 122, and a sealing rubber ring 127 is provided in the groove. By fitting two opposite side walls of the main gear 121 and the sub-gear 122 together, the first recess 1273 and the second recess 1274 on the sealing rubber ring 127 and the guide recess 1270 cooperate with the protrusion on the main gear 121 and the side wall of the main gear 121 to form a first chamber 128 and a second chamber 129.

[0089] Furthermore, the embodiment of the present utility model further discloses a gear assembly 10 , wherein one of the main gear 121 and the secondary gear 122 is rotatably connected to the driven shaft 123 , and the other is rigidly connected to the driven shaft 123 .

[0090] Specifically, in this embodiment, the main gear 121 is interference-fitted on the driven shaft 123, and the sub-gear 122 is rotatably connected to the driven shaft 123, so that the main gear 121 can transmit the power transmitted by the driving wheel 100, and the sub-gear 122 can form a scissor gear with the main gear 121 through hydraulic adjustment, so as to eliminate backlash and reduce vibration when the driving wheel 100 is driving. Of course, in another embodiment, the main gear 121 can also be assembled on the driven shaft 123 by key connection, and those skilled in the art can design it according to actual conditions and specific needs, and this embodiment does not specifically limit this.

[0091] More specifically, in one embodiment, the main gear 121 is freely rotatably sleeved on the driven shaft 123, and the sub-gear 122 is interference fitted on the driven shaft 123, so that the sub-gear 122 can transmit the power transmitted by the driving wheel 100, and the main gear 121 can form a scissors gear with the sub-gear 122 through hydraulic adjustment, thereby eliminating backlash and reducing vibration when the driving wheel 100 is transmitting.

[0092] In the gear assembly 10 provided in the embodiment of the present utility model, as Figures 1 to 4 As shown, it includes a driving wheel 100 and a driven wheel set 120 meshing with each other, the driving wheel 100 is arranged on the driving shaft 110, and the driven wheel set 120 includes a main gear 121 and a sub-gear 122 arranged side by side on the driven shaft 123, and the two side walls of the main gear 121 and the sub-gear 122 facing each other are in contact with each other; the driving shaft 110 and the driven shaft 123 are parallel to each other, and the main gear 121 and the sub-gear 122 are both meshed with the driving wheel 100; the main gear 121 and the sub-gear 122 can rotate around The axis of the driven shaft 123 rotates relatively, the main gear 121 is rigidly connected to the driven shaft 123 by interference fit, the sub gear 122 is rotatably connected to the driven shaft 123, a hydraulic cavity 1210 extending along the circumference of the main gear 121 is provided on the side wall of the main gear 121 close to the sub gear 122, and a first oil circuit 1211 and a second oil circuit 1212 connected to the hydraulic cavity 1210 are provided at both ends of the hydraulic cavity 1210; a sliding portion 1220 is provided on the side wall of the sub gear 122 close to the main gear 121.

[0093] In the gear assembly 10 provided in the embodiment of the present utility model, as Figure 5 and Figure 6As shown, a sealing rubber ring 127 is interference-fitted in the hydraulic chamber 1210, and a first oil hole 1271 and a second oil hole 1272 are provided at both ends of the sealing rubber ring 127. The first oil hole 1271 and the second oil hole 1272 are matched and connected with one end of the first oil passage 1211 and the second oil passage 1212 provided at both ends of the hydraulic chamber 1210, and a guide recess 1270 is provided in the middle of the rubber sealing ring, and a first recess 1273 and a second recess 1274 are provided on both sides of the guide recess 1270. Therefore, the guide recess 1270 is interference-fitted with the sliding portion 1220 formed on the sub-gear 122, so that two independent first chambers 128 and second chambers 129 are formed at both ends of the hydraulic chamber 1210.

[0094] In the gear assembly 10 provided in the embodiment of the present utility model, as Figure 7 As shown, a first auxiliary oil circuit 1230 is formed at a position corresponding to the first oil circuit 1211 on the driven shaft 123, and a second auxiliary oil circuit 1231 is formed at a position corresponding to the second oil circuit 1212; the first auxiliary oil circuit 1230 and the second auxiliary oil circuit 1231 extend along the length direction of the driven shaft 123, and oil injection ports 1232 are provided at both ends of the driven shaft 123. One end of the first auxiliary oil circuit 1230 is connected to the other end of the first oil circuit 1211, and one end of the second auxiliary oil circuit 1231 is connected to the other end of the second oil circuit 1212, and the other end of the first auxiliary oil circuit 1230 and the other end of the second auxiliary oil circuit 1231 are respectively connected to the oil injection ports 1232 at both ends of the driven shaft 123.

[0095] In the gear assembly 10 provided in the embodiment of the present utility model, as Figure 2 and Fig. 9 As shown, the secondary gear 122 is rotatably connected to the driven shaft 123 with clearance, and the driven shaft 123 is axially pressed by a thrust plate 126.

[0096] In the gear assembly 10 provided in the embodiment of the present utility model, as Figure 2 and Figure 8 As shown, the oil filling ports 1232 at both ends of the driven shaft 123 are respectively bolted to the first oil port blocking device 124 and the second oil port blocking device 125 of different pressures, and different pressures are applied to the hydraulic oil in the independent first chamber 128 and the second chamber 129, so that a pressure difference is formed between the first chamber 128 and the second chamber 129. Therefore, through the pressure difference between the first chamber 128 and the second chamber 129, the sliding part 1220 is turned to a chamber with lower pressure, so that the main gear 121 and the auxiliary gear 122 form a scissors gear, so as to eliminate gap and reduce shock when the driving wheel 100 is transmitted.

[0097] During the use of the gear assembly 10 provided in the embodiment of the utility model, as Figure 8As shown, the pressure P1 (bar) of the first oil port blocking device 124 and the pressure P2 (bar) of the second oil port blocking device 125 are first selected, and then the hydraulic oil passes through Figure 7 The oil is injected into the oil filling ports 1232 at the left and right ends of the driven shaft 123, passes through the first auxiliary oil passage 1230 and the second auxiliary oil passage 1231, and then passes through the Figure 3 The first oil passage 1211 and the second oil passage 1212 on both sides of the main gear 121 flow to Figure 5 The first chamber 128 and the second chamber 129 shown. Figure 6 The guide recess 1270 on the sealing rubber ring 127 shown in FIG. Figure 4 The sliding portion 1220 on the sub-gear 122 shown in the figure is installed by interference fit, and the guide recess 1270 of the sealing rubber ring 127 is elastically squeezed by the sliding portion 1220 on the sub-gear 122, so that Figure 5 The first oil chamber and the second oil chamber shown are independent of each other.

[0098] During the use of the gear assembly 10 provided in the embodiment of the utility model, as Figure 8 As shown, assuming that the pressure P1 (bar) of the first oil port blocking device 124 is higher than the pressure P2 (bar) of the second oil port blocking device 125, therefore, Figure 5 The hydraulic oil pressure in the first oil chamber will be higher than the hydraulic oil pressure in the second oil chamber, so the pressure difference will act on Figure 4 The sliding portion 1220 shown generates thrust, causing the pinion 122 to rotate, thereby causing the pinion 122 to contact the other side of the meshing teeth of the driving wheel 100, offsetting the thrust caused by the pressure difference, thereby forming a preload force F and a torsional stiffness K for the pinion 122 to rotate back.

[0099] For the preload force F and torsional stiffness K, assuming that the hydraulic oil temperature remains unchanged, the preload force F and torsional stiffness K can be accurately obtained by the following formula;

[0100] Formula 1: P1×V1=P11×V11

[0101] Formula 2: P2×V2=P22×V22

[0102] Formula 3: P = P11-P22 = P1×V1÷V11-P2×V2÷V22

[0103] Formula 4: f = u × N

[0104] Formula 5: F = P × Sf

[0105] Formula 6: K = {[P1×V1÷(V11-V0)-P2×V2÷(V22+V0)]×Sf}×R

[0106] In the above formula, P1 is Figure 8 The pressure of the first oil port blocking device 124 shown;

[0107] V1 is Figure 8 The volume of the first oil port blocking device 124 selected in the above method is plugged into the oil filling port 1232;

[0108] P2 is Figure 8 The pressure of the second oil port blocking device 125 shown;

[0109] V2 is Figure 8 The volume of the second oil port blocking device 125 selected in the above method is plugged into the oil filling port 1232;

[0110] P11 is Figure 5 The pressure of the hydraulic oil in the first chamber 128;

[0111] V11 is Figure 5 The first chamber 128, Figure 7 The first auxiliary oil circuit 1230, Figure 3 The total volume of the first oil passage 1211;

[0112] P22 is Figure 5 The pressure of the hydraulic oil in the second chamber 129;

[0113] V22 is Figure 5 The second chamber 129, Figure 7 The second auxiliary oil circuit 1231, Figure 3 The total volume of the second oil passage 1212;

[0114] P is Figure 5 The pressure difference of the hydraulic oil in the first chamber 128 and the second chamber 129;

[0115] V0 is Figure 4 The volume of the sliding portion 1220 of the middle pinion 122 within the range of 1 rad with the driven shaft 123 as the center, rad is radians, and 1 rad is approximately equal to a rotation of 57.3 degrees;

[0116] S is Figure 4 The cross-sectional area of ​​the sliding portion 1220 of the middle pinion 122;

[0117] f is Figure 6 The guide recess 1270 of the middle sealing rubber ring 127 is Figure 4 The friction between the sliding part 1220 of the middle pinion 122;

[0118] u is Figure 6 The guide recess 1270 of the middle sealing rubber ring 127 is Figure 4 The friction coefficient between the sliding parts 1220 of the middle sub-gear 122;

[0119] N is Figure 6 The guide recess 1270 of the middle sealing rubber ring 127 is Figure 4 The positive pressure between the sliding part 1220 of the middle sub-gear 122 can be obtained by the extrusion amount of the guide recess 1270 of the sealing rubber ring 127, that is, the elastic deformation amount. The elastic deformation amount is the strain, and the positive pressure is the stress. Therefore, the positive pressure can be obtained according to the formula that the elastic modulus is equal to the stress divided by the strain;

[0120] F is the pre-tightening force of the secondary gear 122 on the driving wheel 100, that is, the pressure difference between the first chamber 128 and the second chamber 129 minus the friction force of the sliding part 1220 and the sealing rubber ring 127 sliding with each other;

[0121] K is the torsional stiffness of the secondary gear 122 rotating backward;

[0122] R is the radius of the geometric center of the hydraulic chamber 1210 (ie, the distance from the geometric center of the hydraulic chamber 1210 to the rotation center of the gear).

[0123] Regarding the above formulas 1 to 6, formula 1 explains that the internal energy applied to the hydraulic oil by the first oil port blocking device 124 is equal to the internal energy of the hydraulic oil in the first chamber 128; formula 2 explains that the internal energy applied to the hydraulic oil by the second oil port blocking device 125 is equal to the internal energy of the hydraulic oil in the second chamber 129; therefore, the pressure difference between the hydraulic oil in the first chamber 128 and the second chamber 129 in formula 3 can be calculated by formulas 1 and 2; the friction force f between the sliding part 1220 and the sealing rubber ring 127 can be calculated by the friction coefficient of the sealing rubber ring 127 and the positive pressure of the sliding part 1220 on the sealing rubber ring 127 in formula 4; the preload force of the secondary gear 122 on the driving wheel 100 can be obtained by subtracting the friction force between the sliding part 1220 and the sealing rubber ring 127 from the pressure difference between the hydraulic oil in the two chambers on the sliding part 1220 in formula 5.

[0124] It can be seen that Formula 6 is able to calculate the torsional stiffness K of the sub-gear 122 rotating backward by substituting the volume of the first oil port blocking device 124 plugged into the oil filling port 1232, the pressure of the first oil port blocking device 124, the volume of the second oil port blocking device 125 plugged into the oil filling port 1232, the pressure of the second oil port blocking device 125, the total volume of the first chamber 128 and the first auxiliary oil circuit 1230 and the first oil circuit 1211, the total volume of the second chamber 129 and the second auxiliary oil circuit 1231 and the second oil circuit 1212, the volume of the sliding portion 1220 within a range of 1rad centered on the driven shaft 123, the cross-sectional area of ​​the sliding portion 1220 and the friction force between the guide recess 1270 of the sealing rubber ring 127 and the sliding portion 1220 of the sub-gear 122 into the formula.

[0125] It should be noted that, in addition to the implementation methods of the utility model described in the above-mentioned specific specific embodiments, those skilled in the art can easily understand other advantages and functions of the utility model from the contents disclosed in this specification. Although the description of the utility model is introduced in conjunction with the preferred embodiment, this does not mean that the features of this utility model are limited to this implementation method. On the contrary, the purpose of introducing the utility model in conjunction with the implementation method is to cover other options or modifications that may be extended based on the claims of the utility model. In order to provide an in-depth understanding of the utility model, the above description contains many specific details, and the utility model can also be implemented without using these details. In addition, in order to avoid confusion or blurring the focus of the utility model, some specific details will be omitted in the description. It should be noted that, in the absence of conflict, the embodiments in the utility model and the features in the embodiments can be combined with each other.

[0126] It should be noted that in this specification, similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined and explained in the subsequent drawings.

[0127] In the description of this embodiment, it should be noted that the terms "upper", "lower", "inner", "bottom", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, or are the orientations or positional relationships in which the utility model product is usually placed when in use. They are only for the convenience of describing the utility model and simplifying the description, and do 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 the utility model.

[0128] The terms “first”, “second”, etc. are only used for distinguishing descriptions and should not be understood as indicating or implying relative importance.

[0129] In the description of this embodiment, it is also necessary to explain that, unless otherwise clearly specified and limited, the terms "set", "connected", 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 mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this embodiment can be understood according to specific circumstances.

[0130] Although the present invention has been illustrated and described with reference to certain preferred embodiments of the present invention, it should be understood by those skilled in the art that the above contents are further detailed descriptions of the present invention in combination with specific embodiments, and it cannot be determined that the specific implementation of the present invention is limited to these descriptions. Those skilled in the art may make various changes in form and details, including making several simple deductions or substitutions, without departing from the spirit and scope of the present invention.

Claims

1. A gear assembly, comprising a driving wheel and a driven wheel group meshing with each other, wherein the driving wheel is arranged on a driving shaft, and the driven wheel group comprises a main gear and a sub-gear arranged side by side on the driven shaft; the driving shaft and the driven shaft are parallel to each other, and the main gear and the sub-gear are both meshed with the driving wheel; characterized in that: The main gear and the auxiliary gear can rotate relative to each other around the axis of the driven shaft; A hydraulic cavity extending along its circumferential direction is formed on one of the two side walls opposite to each other of the main gear and the auxiliary gear, and a sliding portion adapted to the hydraulic cavity is provided on the other side wall; wherein an end of the sliding portion is movably inserted into the hydraulic cavity to separate the hydraulic cavity into a first chamber and a second chamber that are sealed from each other, and there is a pressure difference between the first chamber and the second chamber.

2. The gear assembly according to claim 1, characterized in that: The hydraulic chamber is configured as a groove formed on the one side wall, and the groove extends along the circumference of the one side wall and around the axis of the driven shaft; The sliding portion is configured as a convex block formed on the other side wall, the convex block protrudes from the other side wall, extends toward the one side wall, and at least the shape of the end portion is adapted to the groove; The end of the protrusion is movably inserted into the groove to separate the groove into the first chamber and the second chamber which are sealed from each other and have variable volumes.

3. The gear assembly according to claim 2, characterized in that: The groove includes a first recess and a second recess located at two ends, and a guide recess located between the first recess and the second recess, wherein a width of the guide recess is smaller than a width of the first recess and the second recess; and The convex block is a protrusion extending along the circumference of the other side wall and around the axis of the driven shaft, and the extension length of the protrusion is smaller than the extension length of the groove; wherein The protrusion is fitted in the groove, and the outer wall of the fitting portion of the protrusion and the guide recess is in sealing contact with the inner side wall of the guide recess.

4. The gear assembly according to any one of claims 1 to 3, characterized in that: In one of the two side walls of the main gear and the auxiliary gear facing each other, a first oil passage is formed near the first chamber, and a second oil passage is formed near the second chamber; wherein, One end of the first oil passage is in communication with the first chamber, and the other end extends to the outside of the side wall of the main gear or the auxiliary gear; One end of the second oil passage is communicated with the second chamber, and the other end extends to the outside of the side wall of the main gear or the auxiliary gear.

5. The gear assembly according to claim 4, characterized in that: A first auxiliary oil circuit is formed on the driven shaft at a position corresponding to the first oil circuit, and a second auxiliary oil circuit is formed at a position corresponding to the second oil circuit; The first auxiliary oil circuit and the second auxiliary oil circuit extend along the length direction of the driven shaft, and both ends of the driven shaft are provided with oil filling ports; in One end of the first auxiliary oil circuit is connected to the other end of the first oil circuit, one end of the second auxiliary oil circuit is connected to the other end of the second oil circuit, and the other end of the first auxiliary oil circuit and the other end of the second auxiliary oil circuit are respectively connected to the oil filling ports at both ends of the driven shaft.

6. The gear assembly according to claim 5, characterized in that: The driven shaft also includes an oil port blocking device, which includes a first oil port blocking device and a second oil port blocking device. The first oil port blocking device and the second oil port blocking device are respectively detachably connected to the oil filling ports at both ends of the driven shaft.

7. The gear assembly according to claim 6, characterized in that: The first oil port blocking device and the second oil port blocking device are respectively threadedly connected to the oil filling ports at both ends of the driven shaft.

8. The gear assembly according to claim 7, characterized in that: The first oil port blocking device and the second oil port blocking device are configured as sealing plugs.

9. The gear assembly according to any one of claims 1 to 3, characterized in that: Two side walls of the main gear and the auxiliary gear facing each other are in contact with each other; and The gear assembly further comprises a sealing rubber ring, which is arranged in the hydraulic cavity and matched with the inner peripheral wall of the hydraulic cavity.

10. The gear assembly according to any one of claims 1 to 3, characterized in that: One of the main gear and the auxiliary gear is rotatably connected to the driven shaft, and the other is rigidly connected to the driven shaft.

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