Gear combined type wedge pressure gearbox

Abstract

The invention relates to a gear combined type wedge pressure gearbox, and belongs to the technical field of gearboxes. Comprising a gearbox shell, an input shaft, an intermediate shaft and an output shaft are arranged in the gearbox shell, multiple sets of input gears and a set of reverse gear driving gears are arranged on the input shaft, multiple sets of output gears are arranged on the output shaft, and multiple sets of input driven gears, output driving gears and a set of reverse gear driven gears are arranged on the intermediate shaft. A group of reverse gear shafts are arranged between the intermediate shaft and the input shaft, a group of reverse gear intermediate gears are arranged on the reverse gear shafts, the reverse gear driven gear is meshed with the reverse gear intermediate gears, and the reverse gear intermediate gears are meshed with the reverse gear driving gear; a group of power coupling mechanisms is arranged between each group of input gears and the input shaft, between each group of output gears and the output shaft, and between the input shaft and the reverse gear driving gear; the problems that an existing automatic gearbox is complex in structure, few in gear and high in oil consumption are solved.

Description

Technical Field

[0001] The invention belongs to the technical field of gearboxes, and in particular relates to a gear combination type wedge pressure gearbox. Background Art

[0002] The gearbox is a mechanism used to change the speed and torque from the engine. It can change the transmission ratio of the output shaft and the input shaft in a fixed or step-by-step manner. However, the existing automatic gearbox has a complex structure, fewer gears, high fuel consumption, and is prone to failure. In addition, the kinetic energy recovery rate of the gearbox used in new energy vehicles is low. In order to solve the above problems, the present invention proposes a gear combination wedge pressure gearbox. Summary of the invention

[0003] The invention overcomes the shortcomings of the prior art and proposes a gear combination type wedge pressure transmission; it solves the problems of the current automatic transmission having a complex structure, fewer gears and higher fuel consumption.

[0004] In order to achieve the above object, the present invention is implemented through the following technical solutions.

[0005] A gear combination type helical wedge pressure gearbox comprises a gearbox housing, wherein an input shaft, an intermediate shaft and an output shaft are arranged inside the gearbox housing, a plurality of input gears and a reverse gear driving gear are arranged on the input shaft, a plurality of output gears are arranged on the output shaft, a plurality of input driven gears, a plurality of output driving gears and a reverse gear driven gear are arranged on the intermediate shaft, the number of input gears is equal to that of input driven gears and they mesh one by one, the number of output driving gears is equal to that of output gears and they mesh one by one, a reverse gear shaft is arranged between the intermediate shaft and the input shaft, a reverse gear intermediate gear is arranged on the reverse gear shaft, the reverse gear driven gear meshes with the reverse gear intermediate gear, and the reverse gear intermediate gear meshes with the reverse gear driving gear; a power coupling mechanism is arranged between each input gear group and the input shaft, a power coupling mechanism is arranged between each output gear group and the output shaft, and a power coupling mechanism is arranged between the input shaft and the reverse gear driving gear.

[0006] Furthermore, a group of power coupling mechanisms corresponding to the input gear on the input shaft is controlled to maintain a coupling state, the input shaft is drivingly connected to the input gear corresponding to this group of power coupling mechanisms, and the input shaft transmits power to the intermediate shaft through this group of input gears and the input driven gear meshing with it; a group of power coupling mechanisms on the output shaft is controlled to maintain a coupling state, the output shaft is drivingly connected to the output gear corresponding to this group of power coupling mechanisms, and the intermediate shaft transmits power to the output shaft through this group of output gears and the output driving gear meshing with it, thereby realizing power transmission from the input shaft to the output shaft and realizing a forward gear. By controlling any group of power coupling mechanisms corresponding to the input gear on any group of input shafts and any group of power coupling mechanisms on the output shaft to maintain a coupling state, different transmission ratios between the input shaft and the output shaft can be realized through one-to-one pairing, thereby realizing forward gears with different transmission ratios.

[0007] Furthermore, a group of power coupling mechanisms corresponding to the reverse gear driving gear on the input shaft is controlled to maintain a coupling state, the input shaft is transmission-connected with the reverse gear driving gear corresponding to this group of power coupling mechanisms, and the input shaft transmits power to the intermediate shaft through the reverse gear driving gear, reverse gear intermediate gear, and reverse gear driven gear that are meshed in sequence; a group of power coupling mechanisms on the output shaft is controlled to maintain a coupling state, the output shaft is transmission-connected with the output gear corresponding to this group of power coupling mechanisms, and the intermediate shaft transmits power to the output shaft through this group of output gears and the output driving gear meshed therewith, thereby realizing power transmission from the input shaft to the output shaft, and the output shaft and the input shaft maintain opposite rotation angles, thereby realizing reverse gear; by controlling different power coupling mechanisms on the output shaft to maintain a coupling state, different transmission ratios between the input shaft and the output shaft can be realized, thereby realizing reverse gears with different transmission ratios.

[0008] Furthermore, the structures of the power coupling mechanisms on the input shaft and the output shaft remain the same.

[0009] Furthermore, the power coupling mechanism between the input shaft and the input gear includes a multi-plate clutch, a pressure plate, a locking plate, a locking ring, and a brake mechanism; the multi-plate clutch is sleeved on the outer side of the input shaft, the outer shell of the multi-plate clutch is fixedly connected to the input gear on the input shaft, and the input gear and the outer shell of the multi-plate clutch rotate synchronously; the outer shell of the multi-plate clutch remains open on the side away from the input gear; friction plates and steel plates are arranged one by one inside the outer shell of the multi-plate clutch, wherein the opening of the outer shell of the multi-plate clutch and the innermost side are both arranged as friction plates; the friction plates and steel plates are both sleeved on the outer side of the input shaft, wherein the friction plates are fixedly arranged on the inner side of the outer shell of the multi-plate clutch, the friction plates and the input shaft can transmit relative to each other, the steel plates and the input shaft are matched through splines, and the steel plates and the input shaft rotate synchronously.

[0010] Furthermore, a pressure plate and a locking plate are sequentially sleeved on the input shaft outside the friction plate at the opening of the shell of the multi-plate clutch. The locking plate is located on the side of the pressure plate away from the friction plate. The pressure plate and the locking plate are matched with the input shaft through splines. A first return spring is sleeved on the outside of the input shaft between the locking plate and the pressure plate. The two ends of the first return spring are respectively connected to the locking plate and the pressure plate.

[0011] Furthermore, four locking grooves arranged in a circular array are provided on the end face of the locking plate close to the pressure plate, and the locking grooves are triangular grooves. Four locking protrusions arranged in a circular array are fixedly provided on the end face of the pressure plate close to the locking plate, and the locking protrusions are triangular block structures. The four locking grooves on the locking plate are provided corresponding to the four locking protrusions on the pressure plate; four reset protrusions arranged in a circular array are fixedly provided on the end face of the locking plate close to the pressure plate, and four reset grooves arranged in a circular array are provided on the end face of the pressure plate close to the locking plate, and the four reset protrusions on the locking plate are respectively plugged into the middle of the inner side of the four reset grooves of the pressure plate; two second reset springs are respectively provided inside each reset groove of the pressure plate, and the two second reset springs are respectively provided on both sides of the reset protrusion, one end of the second reset spring is fixedly connected to the inner wall of the reset groove, and the other end of the second reset spring is in sliding contact with the reset protrusion.

[0012] Furthermore, a locking ring is sleeved on the outer side of the locking plate, and the outer cylindrical surface of the locking ring is rotatably connected to the inside of the gearbox housing, and the inner cylindrical surface of the locking ring is provided with four locking protrusions arranged in a circular array, the outer side surface of the locking protrusion is an arc surface, and the arc surface on the outer side of the locking protrusion maintains sliding contact with the outer cylindrical surface of the locking plate; two convex locking grooves are provided on the arc surface on the outer side of each locking protrusion, and an inner concave locking groove is provided on the inner side surface of the locking ring between the two locking protrusions; an annular clamping groove is provided on the input shaft on the inner side of the locking plate, and the cross-section of the clamping groove is a triangular structure, the inner wall of the clamping groove on the side close to the pressure plate is perpendicular to the axis of the input shaft, and the inner wall of the clamping groove on the side away from the pressure plate is a conical surface, and the outer diameter of the conical surface close to the pressure plate is smaller than the outer diameter of the conical surface away from the pressure plate; four internally and externally connected action grooves are provided on the locking plate, and the four action grooves are connected. The grooves are arranged in a circular array along the axis of the locking disk, and the action grooves are arranged along the radial direction of the locking disk; an outer expansion groove is arranged in the middle of the action groove, and the inner diameter of the outer expansion groove is larger than the inner diameter of the action groove; the four action grooves correspond to the four locking protrusions one by one; an action rod is slidably inserted in the inside of the action groove, and a circular outer expansion ring is fixedly arranged on the outer side of the middle part of the action rod, and the outer expansion ring is located on the inner side of the outer expansion groove; the end of the action rod extending to the inner side of the locking disk is a triangular structure; a third return spring is sleeved on the outside of the action rod, and the third return spring is located inside the outer expansion groove, one end of the third return spring is fixedly connected to the inner wall of the outer expansion groove on the side close to the axis of the locking disk, and the other end of the third return spring is fixedly connected to the outer expansion ring; a first spring steel ball is arranged on the end face of the end of the action rod extending to the outside of the locking disk, and the first spring steel ball is clamped in the outer convex locking groove or the inner concave locking groove of the locking ring.

[0013] Furthermore, the brake mechanism is arranged on the outside of the locking ring, and the brake mechanism includes a brake electromagnet, a slide, and a brake pad. The brake electromagnet is fixedly arranged on the inner wall of the gearbox housing, and the active end of the brake electromagnet is fixedly provided with a slide toward the outer cylindrical surface of the locking ring. A brake pad is slidably arranged on the slide, and the brake pad is slidably arranged along the axis of the locking ring.

[0014] Furthermore, an action plate is fixedly arranged on the end face of the locking plate on the side away from the pressure plate, and the action plate is located on the side of the locking ring away from the multi-plate clutch; a plurality of outer electromagnets are fixedly arranged at the outer edge of the end face of the action plate close to the locking ring, and a plurality of inner electromagnets are arranged at a height on the outer cylindrical surface of the locking ring, and the number of the outer electromagnets is the same as the inner electromagnets and they are arranged alternately; a locking plate is sleeved on the outer side of the input shaft between the pressure plate and the locking plate, and the locking plate and the input shaft are matched through splines so that the locking plate and the input shaft rotate synchronously; a plurality of avoidance grooves are arranged on the locking plate, and the locking protrusions and reset protrusions are avoided by the avoidance grooves; a circle of card points is arranged at the outer edge of the locking plate for engaging with the outer shell of the multi-plate clutch; four circular arrays of second spring steel balls are arranged on the end face of the locking ring facing the outer shell of the multi-plate clutch, and the second spring steel balls are used to cooperate with the locking plate.

[0015] The beneficial effects of the present invention compared with the prior art are as follows:

[0016] The present invention provides a gear-combined helical wedge pressure transmission, which can achieve different transmission ratios by pairing different power coupling mechanisms on the input shaft and the power coupling mechanisms on the output shaft, thereby increasing the number of gears and better meeting the actual working conditions of the automobile, thereby reducing fuel consumption; applying the transmission provided by the present invention to new energy vehicles is beneficial to speed shifting and kinetic energy recovery. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The present invention will be further described in detail below in conjunction with the accompanying drawings:

[0018] Figure 1 It is a schematic diagram of the overall structure of the present invention;

[0019] Figure 2 It is a structural schematic diagram of the power coupling mechanism;

[0020] Figure 3 is a plan view of a pressure plate;

[0021] Figure 4 is a plan view of the locking disk;

[0022] Figure 5 is a schematic diagram of the structure between the reset protrusion, two second reset springs and the reset groove;

[0023] Figure 6 is a schematic diagram of the change of the locking protrusion and the locking groove from an uncoupled state to a coupled state;

[0024] Figure 7 It is a schematic diagram of the relative relationship between the input shaft, locking plate, locking ring, and action plate;

[0025] Figure 8 It is a side view of the input shaft, locking plate, pressure plate, locking ring, and brake mechanism;

[0026] Fig. 9 is a plan view of the locking plate;

[0027] Fig.10 is a schematic diagram of the arrangement of the locking electromagnet;

[0028] Among them, 1 is the input shaft, 2 is the intermediate shaft, 3 is the output shaft, 4 is the input gear, 5 is the output gear, 6 is the reverse gear driving gear, 7 is the input driven gear, 8 is the output driving gear, 9 is the reverse gear driven gear, 10 is the reverse shaft, 11 is the reverse gear intermediate gear, 12 is the power coupling mechanism, 13 is the multi-plate clutch, 14 is the friction plate, 15 is the steel plate, 16 is the pressure plate, 17 is the locking plate, 18 is the locking groove, 19 is the locking convex block, 20 is the reset groove, 21 is the reset convex block, 22 is the second reset spring, 2 3 is a locking ring, 24 is a gearbox housing, 25 is a locking protrusion, 26 is an outer convex locking groove, 27 is an inner concave locking groove, 28 is a clamping groove, 29 is an action groove, 30 is an outer expansion groove, 31 is an action rod, 32 is an outer expansion ring, 33 is a third return spring, 34 is a first spring steel ball, 35 is a brake electromagnet, 36 is a slide, 37 is a brake pad, 38 is an action disc, 39 is an outer electromagnet, 40 is an inner electromagnet, 41 is a locking plate, 42 is a clamping point, 43 is a second spring steel ball, and 44 is a locking electromagnet. DETAILED DESCRIPTION

[0029] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention clearer, the present invention is further described in detail in conjunction with the embodiments and the accompanying drawings. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention. The technical solutions of the present invention are described in detail below in conjunction with the embodiments and the accompanying drawings, but the scope of protection is not limited thereto.

[0030] like Figure 1As shown in FIG. 10 , the present invention provides a gear combination helical wedge pressure gearbox, including a gearbox housing 24, wherein an input shaft 1, an intermediate shaft 2, and an output shaft 3 are arranged inside the gearbox housing 24, multiple groups of input gears 4 and a group of reverse gear driving gears 6 are arranged on the input shaft 1, multiple groups of output gears 5 are arranged on the output shaft 3, multiple groups of input driven gears 7, multiple groups of output driving gears 8, and a group of reverse gear driven gears 9 are arranged on the intermediate shaft 2, the number of input gears 4 and input driven gears 7 are equal and meshed one by one, and the output driving gears 8 and output driven gears 9 are meshed one by one. The number of gears 5 is equal and they are meshed one by one. A reverse gear shaft 10 is provided between the intermediate shaft 2 and the input shaft 1. A reverse gear intermediate gear 11 is provided on the reverse gear shaft 10. The reverse gear driven gear 9 is meshed with the reverse gear intermediate gear 11. The reverse gear intermediate gear 11 is meshed with the reverse gear driving gear 6. A power coupling mechanism 12 is provided between each set of input gears 4 and the input shaft 1, a power coupling mechanism 12 is provided between each set of output gears 5 and the output shaft 3, and a power coupling mechanism 12 is provided between the input shaft 1 and the reverse gear driving gear 6.

[0031] A group of power coupling mechanisms 12 corresponding to the input gear 4 on the input shaft 1 is controlled to maintain a coupling state, and the input shaft 1 is connected to the input gear 4 corresponding to the group of power coupling mechanisms 12 in a transmission connection, and the input shaft 1 transmits power to the intermediate shaft 2 through the group of input gears 4 and the input driven gear 7 meshing with the group of input gears 4; a group of power coupling mechanisms 12 on the output shaft 3 is controlled to maintain a coupling state, and the output shaft 3 is connected to the output gear 5 corresponding to the group of power coupling mechanisms 12 in a transmission connection, and the intermediate shaft 2 transmits power to the output shaft 3 through the group of output gears 5 and the output driving gear 8 meshing with the group of output gears 5, thereby realizing power transmission from the input shaft 1 to the output shaft 3 and realizing a forward gear. By controlling any group of power coupling mechanisms 12 corresponding to the input gear 4 on any group of input shafts 1 and any group of power coupling mechanisms 12 on the output shaft 3 to maintain a coupling state, different transmission ratios between the input shaft 1 and the output shaft 3 can be realized through one-to-one pairing, thereby realizing forward gears with different transmission ratios.

[0032] A group of power coupling mechanisms 12 corresponding to the reverse gear driving gear 6 on the input shaft 1 is controlled to maintain a coupling state, and the input shaft 1 is connected to the reverse gear driving gear 6 corresponding to this group of power coupling mechanisms 12 in a transmission connection, and the input shaft 1 transmits power to the intermediate shaft 2 through the reverse gear driving gear 6, the reverse gear intermediate gear 11, and the reverse gear driven gear 9 that are meshed in sequence; a group of power coupling mechanisms 12 on the output shaft 3 is controlled to maintain a coupling state, and the output shaft 3 is connected to the output gear 5 corresponding to this group of power coupling mechanisms 12 in a transmission connection, and the intermediate shaft 2 transmits power to the output shaft 3 through this group of output gears 5 and the output driving gear 8 meshed therewith, thereby realizing power transmission from the input shaft 1 to the output shaft 3, and the output shaft 3 and the input shaft 1 maintain opposite rotation squares, realizing reverse gear. By controlling different power coupling mechanisms 12 on the output shaft 3 to maintain a coupling state, different transmission ratios between the input shaft 1 and the output shaft 3 can be realized, thereby realizing reverse gears with different transmission ratios.

[0033] The structures of the power coupling mechanisms 12 on the input shaft 1 and the output shaft 3 remain the same, and both include a multi-plate clutch 13, a pressure plate 16, a locking plate 17, a locking ring 23, and a brake mechanism.

[0034] The following is an introduction based on the power coupling mechanism 12 on the input shaft 1:

[0035] The multi-plate clutch 13 is sleeved on the outside of the input shaft 1, and the housing of the multi-plate clutch 13 is fixedly connected to the input gear 4 on the input shaft 1, and the input gear 4 and the housing of the multi-plate clutch 13 rotate synchronously. The housing of the multi-plate clutch 13 is open on the side away from the input gear 4. Inside the housing of the multi-plate clutch 13, there are staggered friction plates 14 and steel plates 15, wherein the opening of the housing of the multi-plate clutch 13 and the innermost side are both provided with friction plates 14; the friction plates 14 and the steel plates 15 are sleeved on the outside of the input shaft 1, wherein the friction plates 14 are fixedly provided on the inner side of the housing of the multi-plate clutch 13, and the friction plates 14 and the input shaft 1 can be relatively driven, and the steel plates 15 and the input shaft 1 are matched through splines, and the steel plates 15 and the input shaft 1 rotate synchronously.

[0036] A pressure plate 16 and a locking plate 17 are sleeved on the input shaft 1 outside the friction plate 14 at the housing opening of the multi-plate clutch 13 in sequence. The locking plate 17 is located on the side of the pressure plate 16 away from the friction plate 14. The pressure plate 16 and the locking plate 17 are matched with the input shaft 1 through splines, so that the locking plate 17 and the pressure plate 16 rotate with the input shaft 1. A first return spring is sleeved on the outside of the input shaft 1 between the locking plate 17 and the pressure plate 16. The two ends of the first return spring are respectively connected to the locking plate 17 and the pressure plate 16. The first return spring provides a tensioning force between the locking plate 17 and the pressure plate 16. When the locking plate 17 and the pressure plate 16 are not subjected to external force, the minimum distance between the two is maintained.

[0037] Four locking grooves 18 arranged in a circular array are provided on the end surface of the locking plate 17 close to the pressure plate 16. The locking grooves 18 are triangular grooves. Four locking protrusions 19 arranged in a circular array are fixedly provided on the end surface of the pressure plate 16 close to the locking plate 17. The locking protrusions 19 are triangular block structures. The four locking grooves 18 on the locking plate 17 are provided correspondingly to the four locking protrusions on the pressure plate 16.

[0038] Four circular arrayed reset convex blocks 21 are fixedly arranged on the end surface of the locking plate 17 near the pressure plate 16, and four circular arrayed reset grooves 20 are arranged on the end surface of the pressure plate 16 near the locking plate 17. The four reset convex blocks 21 on the locking plate 17 are respectively inserted into the middle of the inner side of the four reset grooves 20 of the pressure plate 16. Two second reset springs 22 are respectively arranged inside each reset groove 20 of the pressure plate 16, and the two second reset springs 22 are respectively arranged on both sides of the reset convex block 21, one end of the second reset spring 22 is fixedly connected to the inner wall of the reset groove 20, and the other end of the second reset spring 22 is in sliding contact with the reset convex block 21.

[0039] When the locking plate 17 and the pressure plate 16 are not subjected to external force, the first reset spring is in a reset state, and a minimum distance is maintained between the locking plate 17 and the pressure plate 16; at this time, the four locking protrusions 19 on the pressure plate 16 are respectively inserted into the four locking grooves 18 on the locking plate 17, and the four reset protrusions 21 on the locking plate 17 are respectively located in the middle of the inner side of the four reset grooves 20 on the pressure plate 16, and the two second reset springs 22 in each reset groove 20 are in a reset state, and the initial distance and initial angle are maintained between the locking plate 17 and the pressure plate 16.

[0040] A locking ring 23 is sleeved on the outer side of the locking disk 17. The locking ring 23 is an annular structure. The outer cylindrical surface of the locking ring 23 is rotatably connected to the inside of the gearbox housing 24. Four locking protrusions 25 arranged in a circular array are arranged on the inner cylindrical surface of the locking ring 23. The outer side surface of the locking protrusion 25 is an arc surface. The arc surface of the outer side of the locking protrusion 25 maintains sliding contact with the outer cylindrical surface of the locking disk 17. Two convex locking grooves 26 are arranged on the arc surface of the outer side of each locking protrusion 25, and an inner concave locking groove 27 is arranged on the inner side surface of the locking ring 23 between the two locking protrusions 25.

[0041] An annular clamping groove 28 is provided on the input shaft 1 on the inner side of the locking plate 17. The cross-section of the clamping groove 28 is a triangular structure. The inner wall of the clamping groove 28 on the side close to the pressure plate 16 is perpendicular to the axis of the input shaft 1, and the inner wall of the clamping groove 28 on the side away from the pressure plate 16 is a conical surface, and the outer diameter of the conical surface close to the pressure plate 16 is smaller than the outer diameter of the conical surface away from the pressure plate 16.

[0042] The locking disk 17 is provided with four action grooves 29 that are connected inside and outside. The four action grooves 29 are arranged in a circular array along the axis of the locking disk 17, and the action grooves 29 are arranged along the radial direction of the locking disk 17. An outward expansion groove 30 is arranged in the middle of the action groove 29, and the inner diameter of the outward expansion groove 30 is larger than the inner diameter of the action groove 29. The four action grooves 29 correspond to the four locking protrusions 25 one by one. An action rod 31 is slidably inserted in the inside of the action groove 29, and a circular outward expansion ring 32 is fixedly arranged on the outside of the middle part of the action rod 31, and the outward expansion ring 32 is located on the inner side of the outward expansion groove 30. The end of the action rod 31 extending into the inner side of the locking disk 17 is a triangular structure. A third return spring 33 is sleeved on the outside of the action rod 31, and the third return spring 33 is located inside the outer expansion groove 30. One end of the third return spring 33 is fixedly connected to the inner wall of the outer expansion groove 30 close to the axis of the locking disk 17, and the other end of the third return spring 33 is fixedly connected to the outer expansion ring 32. The third return spring 33 provides a tendency for the action rod 31 to slide toward the outside of the locking disk 17. A first spring steel ball 34 is arranged on the end surface of one end of the action rod 31 extending to the outside of the locking disk 17, and the first spring steel ball 34 is clamped in the outer convex locking groove 26 or the inner concave locking groove 27 of the locking ring 23.

[0043] The brake mechanism is arranged on the outer side of the locking ring 23, and includes a brake electromagnet 35, a slide 36, and a brake pad 37. The brake electromagnet 35 is fixedly arranged on the inner wall of the gearbox housing 24. The action end of the brake electromagnet 35 is fixedly provided with a slide 36 facing the outer cylindrical surface of the locking ring 23. The brake pad 37 is slidably arranged on the slide 36, and the brake pad 37 is slidably arranged along the axis of the locking ring 23. When braking is required, the brake electromagnet 35 is energized to extend the slide 36, and the slide 36 drives the brake pad 37 to move until the brake pad 37 is in stable contact with the outer side of the locking ring 23, so that the locking ring 23 cannot continue to rotate and the brake is achieved.

[0044] An action disc 38 is fixedly arranged on the end face of the locking disc 17 away from the pressure disc 16, and the action disc 38 is located on the side of the locking ring 23 away from the multi-plate clutch 13. A plurality of outer electromagnets 39 are fixedly arranged at the outer edge of the end face of the action disc 38 close to the locking ring 23, and a plurality of inner electromagnets 40 are arranged at a height on the outer cylindrical surface of the locking ring 23, and the number of the outer electromagnets 39 and the inner electromagnets 40 are the same and are arranged alternately.

[0045] A locking plate 41 is sleeved on the outside of the input shaft 1 between the pressure plate 16 and the locking plate 17. The locking plate 41 and the input shaft 1 are matched through splines, so that the locking plate 41 and the input shaft 1 rotate synchronously. A plurality of avoidance grooves are provided on the locking plate 41, and the locking protrusions 19 and the reset protrusions 21 are avoided through the avoidance grooves. A circle of card points 42 is provided at the outer edge of the locking plate 41 for fitting with the outer shell of the multi-plate clutch 13.

[0046] Four second spring steel balls 43 in a circular array are arranged on the end surface of the locking ring 23 facing the housing of the multi-plate clutch 13 . The second spring steel balls 43 are used to cooperate with the locking plate 41 .

[0047] The connection structure between the locking plate 41 and the locking disk 17 can also adopt a locking electromagnet 44, one end of the locking electromagnet 44 is fixed on the locking disk 17, and the other end of the locking electromagnet 44 is fixed on the locking plate 41. When the locking electromagnet 44 is energized, the locking plate 41 is pushed out, and when the locking electromagnet 44 is energized again, the locking plate 42 is pulled back.

[0048] The working principle of the power coupling mechanism 12 is:

[0049] When the power coupling mechanism 12 is in an uncoupled state, the first spring steel balls 34 at the outer ends of the four action rods 31 are respectively engaged with the four concave locking grooves 27 on the inner side of the locking ring 23, so that the action rods 31 slide toward the outer side of the locking plate 17 under the action of the third return spring 33, so that the inner ends of the action rods 31 are disengaged from the engaging grooves 28 of the input shaft 1. Since the inner ends of the action rods 31 do not interact with the engaging grooves 28 of the input shaft 1, the locking plate 17 remains in the initial position without sliding along the axial direction of the input shaft 1. The locking plate 17 and the pressure plate 16 both maintain their initial angles and positions. At this time, the first reset spring is in the reset state, and the locking plate 17 and the pressure plate 16 maintain the minimum distance. At this time, the four locking protrusions 19 on the pressure plate 16 are respectively inserted into the four locking grooves 18 on the locking plate 17, and the four reset protrusions 21 on the locking plate 17 are respectively located in the middle of the inner side of the four reset grooves 20 on the pressure plate 16. The two second reset springs 22 in each reset groove 20 are in the reset state. At this time, the pressure plate 16 and the outermost friction plate 14 of the multi-plate clutch 13 remain disengaged, and the friction plate 14 and the steel plate 15 inside the multi-plate clutch 13 also remain disengaged. At this time, the locking plate 41 and the outer shell of the multi-plate clutch 13 also remain disengaged. The input shaft 1 drives the locking plate 17, the pressure plate 16, the locking plate 41 and the steel plate 15 of the multi-plate clutch 13 to rotate, and the pressure plate 16 and the steel plate 15 cannot transmit power to the friction plate 14 of the multi-plate clutch 13, so that the housing of the multi-plate clutch 13 cannot rotate, and the housing of the multi-plate clutch 13 cannot drive the input gear 4 to rotate, so that the power coupling mechanism 12 is in an uncoupled state. When the locking plate 17 rotates, the first spring steel ball 34 at one end of the outer side of the action rod 31 is engaged with the inner concave locking groove 27 on the inner side of the locking ring 23, thereby driving the locking ring 23 to rotate synchronously.

[0050] When the power coupling mechanism 12 needs to be coupled, the brake mechanism is controlled to operate so that the locking ring 23 cannot rotate, while the locking plate 17 continues to rotate under the drive of the input shaft 1, so that the locking plate 17 rotates relative to the locking ring 23, and the four action rods 31 on the locking plate 17 also rotate synchronously with the locking plate 17, so that the first spring steel ball 34 at the outer end of the action rod 31 escapes from the concave locking groove 27 on the inner side of the locking ring 23, and slides on the inner side surface of the locking ring 23 until it is engaged with the first convex locking groove 26 of the locking protrusion 25 of the locking ring 23. At this time, the brake mechanism stops braking, so that the locking ring 23 and the locking plate 17 rotate synchronously again. As the first spring steel ball 34 at the outer end of the action rod 31 moves from the concave locking groove 27 to the convex locking groove 26, the action rod 31 slides toward the inner side of the locking plate 17, so that the triangular structure at the inner end of the action rod 31 is inserted into the clamping groove 28 of the input shaft 1, and the inclined surface of the triangular structure cooperates with the conical surface of the clamping groove 28, so that the action rod 31 slides toward the side of the pressure plate 16, and the action rod 31 drives the locking plate 17 to slide toward the side of the pressure plate 16, and the locking plate 17 drives the locking ring 23 to slide toward the side of the pressure plate 16 synchronously, and the locking plate 17 squeezes the pressure plate 16 through the locking plate 41, and the squeezed pressure plate 16 squeezes the outermost friction plate 14 of the multi-plate clutch 13, and the friction plate 14 squeezes the inner steel plate 15, and the transmission is passed in sequence until the friction plate 14 and the steel plate 15 make initial contact. At this time, the input shaft 1 drives the locking plate 17, the locking plate 41, the pressure plate 16, and the steel plate 15 to rotate, and the locking plate 17 and the pressure plate 16 are relatively misaligned in angle, so that the locking protrusion 19 on the pressure plate 16 and the locking groove 18 on the locking plate 17 are relatively misaligned, and the inclined surface on the locking protrusion 19 and the inclined surface of the locking groove 18 interact and squeeze, so that the pressure plate 16 continues to slide and squeeze toward one side of the multi-plate clutch 13, so that the pressure plate 16 is in close contact with the left outer friction plate 14, and the friction plate 14 is in close contact with the steel plate 15, so that the pressure plate 16 and the steel plate 15 can drive the friction plate 14 to rotate, and the friction plate 14 drives the outer shell of the multi-plate clutch 13 to rotate, and the outer shell of the multi-plate clutch 13 drives the input gear 4 to rotate, thereby entering a coupled state.In order to ensure the stability of the power coupling mechanism 12, the outer electromagnet 39 and the inner electromagnet 40 are energized to make the locking ring 23 rotate relative to the locking disk 17, and the first spring steel ball 34 at the outer end of the action rod 31 enters into the second outer convex locking latch of the locking protrusion 25. During the rotation of the locking ring 23, the second spring steel ball 43 on the outer side of the locking ring 23 contacts the locking plate 41, thereby squeezing the locking plate 41, and the card point 42 on the outer side of the locking plate 41 is engaged with the outer shell of the multi-plate clutch 13, so that the locking plate 41 can directly drive the outer shell of the multi-plate clutch 13 to rotate, and directly drive the input gear 4 to rotate, so as to keep the power coupling mechanism 12 from accidentally being uncoupled when encountering a large load.

[0051] When the power coupling mechanism 12 needs to be released from the coupled state to the uncoupled state, the control brake mechanism brakes again, so that the first spring steel ball 34 at the outer end of the action rod 31 is re-engaged from the second convex locking groove 26 of the locking protrusion 25 to the inner concave locking groove 27, and the inner end of the action rod 31 is disengaged from the engaging groove 28 of the input shaft 1 under the rebound force of the third return spring 33. Under the rebound force of the steel plate 15 and the friction plate 14 of the multi-plate clutch 13, the pressure plate 16 and the locking plate 17 slide toward the side away from the multi-plate clutch 13, so that the steel plate 15 and the friction plate 14 and the friction plate 14 and the pressure plate 16 are disengaged, and the locking plate 17 returns to the initial position. Under the action of the first return spring and the second return spring 22, the locking protrusion corresponds to the locking groove 18 again and is engaged again. In this way, the power coupling mechanism 12 is restored to the uncoupled state, and the input shaft 1 can no longer drive the input gear 4 to rotate.

[0052] It will be apparent to those skilled in the art that the invention is not limited to the details of the exemplary embodiments described above and that the invention can be implemented in other specific forms without departing from the spirit or essential features of the invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description, and it is intended that all variations falling within the meaning and scope of the equivalent elements of the claims be included in the invention. Any reference numeral in a claim should not be considered as limiting the claim to which it relates.

Claims

1. A gear combination wedge pressure gearbox, characterized in that: The invention comprises a gearbox housing (24), wherein an input shaft (1), an intermediate shaft (2), and an output shaft (3) are arranged inside the gearbox housing (24); a plurality of input gears (4) and a reverse gear driving gear (6) are arranged on the input shaft (1); a plurality of output gears (5) are arranged on the output shaft (3); a plurality of input driven gears (7), a plurality of output driving gears (8), and a reverse gear driven gear (9) are arranged on the intermediate shaft (2); the number of input gears (4) and input driven gears (7) are equal and mesh with each other; the number of output driving gears (8) and output gears (5) are equal and mesh with each other; A set of reverse gear shafts (10) is arranged between the intermediate shaft (2) and the input shaft (1), a set of reverse gear intermediate gears (11) is arranged on the reverse gear shaft (10), the reverse gear driven gear (9) is meshed with the reverse gear intermediate gear (11), and the reverse gear intermediate gear (11) is meshed with the reverse gear driving gear (6); a set of power coupling mechanisms (12) is arranged between each set of input gears (4) and the input shaft (1), a set of power coupling mechanisms (12) is arranged between each set of output gears (5) and the output shaft (3), and a set of power coupling mechanisms (12) is arranged between the input shaft (1) and the reverse gear driving gear (6).

2. The gear combination type wedge pressure transmission according to claim 1, characterized in that: A group of power coupling mechanisms (12) on the input shaft (1) corresponding to the input gear (4) are controlled to maintain a coupling state, the input shaft (1) is drivingly connected to the input gear (4) corresponding to the group of power coupling mechanisms (12), and the input shaft (1) transmits power to the intermediate shaft (2) through the group of input gears (4) and the input driven gear (7) meshing therewith; a group of power coupling mechanisms (12) on the output shaft (3) are controlled to maintain a coupling state, the output shaft (3) is drivingly connected to the output gear (5) corresponding to the group of power coupling mechanisms (12), and the intermediate shaft ( 2) Power is transmitted to the output shaft (3) through the set of output gears (5) and the output driving gear (8) meshing therewith, thereby realizing power transmission from the input shaft (1) to the output shaft (3), and realizing a forward gear; controlling any set of power coupling mechanisms (12) corresponding to the input gears (4) on any set of input shafts (1) and any set of power coupling mechanisms (12) on the output shaft (3) to maintain a coupled state, and through one-to-one pairing, different transmission ratios between the input shaft (1) and the output shaft (3) can be realized, thereby realizing forward gears with different transmission ratios.

3. The gear combination type wedge pressure transmission according to claim 1, characterized in that: A group of power coupling mechanisms (12) on the input shaft (1) corresponding to the reverse gear driving gear (6) is controlled to maintain a coupling state, the input shaft (1) is drivingly connected with the reverse gear driving gear (6) corresponding to the group of power coupling mechanisms (12), and the input shaft (1) transmits power to the intermediate shaft (2) through the reverse gear driving gear (6), the reverse gear intermediate gear (11), and the reverse gear driven gear (9) that are meshed in sequence; a group of power coupling mechanisms (12) on the output shaft (3) is controlled to maintain a coupling state, the output shaft (3) is drivingly connected with the reverse gear driving gear (6), the reverse gear intermediate gear (11), and the reverse gear driven gear (9) that are meshed in sequence. The intermediate shaft (2) is connected to the output gear (5) through a group of output gears (5) and an output driving gear (8) meshing therewith, thereby realizing power transmission from the input shaft (1) to the output shaft (3), and the output shaft (3) and the input shaft (1) maintain opposite rotational directions, thereby realizing reverse gear; by controlling different power coupling mechanisms (12) on the output shaft (3) to maintain a coupling state, different transmission ratios between the input shaft (1) and the output shaft (3) can be realized, thereby realizing reverse gears with different transmission ratios.

4. The gear combination type wedge pressure transmission according to claim 1, characterized in that: The structures of the power coupling mechanisms (12) on the input shaft (1) and the output shaft (3) remain the same.

5. The gear combination type wedge pressure transmission according to claim 4, characterized in that: The power coupling mechanism (12) between the input shaft (1) and the input gear (4) comprises a multi-plate clutch (13), a pressure plate (16), a locking plate (17), a locking ring (23), and a brake mechanism; the multi-plate clutch (13) is sleeved on the outer side of the input shaft (1), the outer shell of the multi-plate clutch (13) is fixedly connected to the input gear (4) on the input shaft (1), and the input gear (4) and the outer shell of the multi-plate clutch (13) rotate synchronously; the outer shell of the multi-plate clutch (13) is open on the side away from the input gear (4); The outer shell of the multi-plate clutch (13) is provided with friction plates (14) and steel plates (15) staggered one by one, wherein the friction plates (14) are arranged at the outer opening of the outer shell of the multi-plate clutch (13) and the innermost side; the friction plates (14) and the steel plates (15) are both sleeved on the outer side of the input shaft (1), wherein the friction plates (14) are fixedly arranged on the inner side of the outer shell of the multi-plate clutch (13), the friction plates (14) and the input shaft (1) can be transmitted relative to each other, the steel plates (15) and the input shaft (1) are matched with each other through splines, and the steel plates (15) and the input shaft (1) rotate synchronously.

6. The gear combination type wedge pressure transmission according to claim 5, characterized in that: A pressure plate (16) and a locking plate (17) are sleeved on the input shaft (1) outside the friction plate (14) at the opening of the shell of the multi-plate clutch (13) in sequence. The locking plate (17) is located on the side of the pressure plate (16) away from the friction plate (14). The pressure plate (16) and the locking plate (17) are matched with the input shaft (1) through splines. A first return spring is sleeved on the outside of the input shaft (1) between the locking plate (17) and the pressure plate (16). The two ends of the first return spring are respectively connected to the locking plate (17) and the pressure plate (16).

7. The gear combination type wedge pressure transmission box according to claim 6, characterized in that: Four locking grooves (18) arranged in a circular array are arranged on one end surface of the locking plate (17) close to the pressure plate (16), and the locking grooves (18) are triangular grooves. Four locking protrusions (19) arranged in a circular array are fixedly arranged on one end surface of the pressure plate (16) close to the locking plate (17), and the locking protrusions (19) are triangular block structures. The four locking grooves (18) on the locking plate (17) are arranged corresponding to the four locking protrusions on the pressure plate (16); four reset protrusions (21) arranged in a circular array are fixedly arranged on the end surface of the locking plate (17) close to the pressure plate (16); four reset grooves (20) arranged in a circular array are arranged on the end surface of the pressure plate (16) close to the locking plate (17); the four reset protrusions (21) on the locking plate (17) are respectively inserted into the middle of the inner side of the four reset grooves (20) of the pressure plate (16); two second reset springs (22) are respectively arranged inside each reset groove (20) of the pressure plate (16); the two second reset springs (22) are respectively arranged on both sides of the reset protrusion (21); one end of the second reset spring (22) is fixedly connected to the inner wall of the reset groove (20), and the other end of the second reset spring (22) is in sliding contact with the reset protrusion (21).

8. The gear combination type wedge pressure transmission box according to claim 5, characterized in that: A locking ring (23) is sleeved on the outer side of the locking disk (17), and the outer cylindrical surface of the locking ring (23) is rotatably connected to the inside of the gearbox housing (24). Four locking protrusions (25) arranged in a circular array are arranged on the inner cylindrical surface of the locking ring (23), and the outer side surface of the locking protrusion (25) is an arc surface. The arc surface on the outer side of the locking protrusion (25) maintains sliding contact with the outer cylindrical surface of the locking disk (17); two external convex locking grooves (26) are arranged on the outer arc surface of each locking protrusion (25), and a locking groove (26) is arranged on the inner side surface of the locking ring (23) between the two locking protrusions (25). An inwardly concave locking groove (27); an annular clamping groove (28) is provided on the input shaft (1) inside the locking plate (17); the cross section of the clamping groove (28) is a triangular structure; the inner wall of the clamping groove (28) on the side close to the pressure plate (16) is perpendicular to the axis of the input shaft (1); the inner wall of the clamping groove (28) on the side away from the pressure plate (16) is a conical surface; the outer diameter of the conical surface on the side close to the pressure plate (16) is smaller than the outer diameter of the conical surface on the side away from the pressure plate (16); four action grooves (29) connected inside and outside are provided on the locking plate (17); the four action grooves (29) are arranged along the axis of the locking plate (17). The action groove (29) is arranged in a circular array, and is arranged along the radial direction of the locking disk (17); an outward expansion groove (30) is arranged in the middle of the action groove (29), and the inner diameter of the outward expansion groove (30) is larger than the inner diameter of the action groove (29); the four action grooves (29) correspond to the four locking protrusions (25) one by one; an action rod (31) is slidably inserted in the inside of the action groove (29), and a circular outward expansion ring (32) is fixedly arranged on the outer side of the middle part of the action rod (31), and the outward expansion ring (32) is located on the inner side of the outward expansion groove (30); the end of the action rod (31) extending into the inner side of the locking disk (17) is a triangular structure; A third return spring (33) is sleeved on the outer side of the action rod (31), and the third return spring (33) is located inside the outer expansion groove (30). One end of the third return spring (33) is fixedly connected to the inner wall of the outer expansion groove (30) close to the axis of the locking disk (17), and the other end of the third return spring (33) is fixedly connected to the outer expansion ring (32); a first spring steel ball (34) is arranged on the end surface of one end of the action rod (31) extending to the outer side of the locking disk (17), and the first spring steel ball (34) is clamped in the outer convex locking groove (26) or the inner concave locking groove (27) of the locking ring (23).

9. The gear combination type wedge pressure transmission box according to claim 8, characterized in that: The brake mechanism is arranged on the outer side of the locking ring (23), and comprises a brake electromagnet (35), a slideway (36), and a brake pad (37). The brake electromagnet (35) is fixedly arranged on the inner wall of the gearbox housing (24), and the action end of the brake electromagnet (35) is fixedly provided with a slideway (36) facing the outer cylindrical surface of the locking ring (23). The brake pad (37) is slidably arranged on the slideway (36), and the brake pad (37) is slidably arranged along the axis of the locking ring (23).

10. The gear combination type wedge pressure transmission box according to claim 9, characterized in that: An action disc (38) is fixedly arranged on the end surface of the locking disc (17) away from the pressure disc (16), and the action disc (38) is located on the side of the locking ring (23) away from the multi-plate clutch (13); a plurality of outer electromagnets (39) are fixedly arranged at the outer edge of the end surface of the action disc (38) close to the locking ring (23), and a plurality of inner electromagnets (40) are arranged at a height on the outer cylindrical surface of the locking ring (23), and the number of the outer electromagnets (39) and the inner electromagnets (40) is the same and they are arranged alternately; a locking plate (41) is sleeved on the outer side of the input shaft (1) between the pressure disc (16) and the locking disc (17) The locking plate (41) and the input shaft (1) are matched through a spline, so that the locking plate (41) and the input shaft (1) rotate synchronously; a plurality of avoidance grooves are provided on the locking plate (41), and the locking protrusions (19) and the reset protrusions (21) are avoided through the avoidance grooves; a circle of card points (42) are provided at the outer edge of the locking plate (41) for engaging with the outer shell of the multi-plate clutch (13); four circular arrays of second spring steel balls (43) are provided on the end surface of the locking ring (23) facing the outer shell of the multi-plate clutch (13), and the second spring steel balls (43) are used to cooperate with the locking plate (41).

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