CN220452673U - Hydrostatic gearbox - Google Patents

Abstract

The utility model discloses a hydrostatic gearbox which comprises a box body, a first input shaft, a second input shaft, an output shaft and a clutch shaft, wherein the first input shaft is in transmission connection with a first hydraulic motor; the first oil pipe supplies oil to a cavity in the clutch shaft through a throttle valve, a first oil throwing hole is formed in the throttle valve, and the first oil throwing hole is positioned between the bearing and the inner wall of the box body; the clutch shaft is also provided with a plurality of second oil throwing holes for throwing oil outwards, and the second oil throwing holes extend radially. The scheme can realize heavy load or light load operation of the loader by coupling the power of the two motors or outputting the power of a single motor; and oil is sprayed to radiate heat for components in the gearbox through an oil pipe.

Description

Hydrostatic gearbox

Technical Field

The utility model relates to the field of loaders, in particular to a hydrostatic gearbox.

Background

The gearbox for the loader of the same type adopts a hydraulic gearbox with single engine input and double changes of the gearbox and a torque converter, and realizes low-speed heavy-duty work and high-speed running through the hydraulic torque converter.

The patent document with publication number CN108518458A discloses a gearbox for a loader, which comprises four planetary rows, four brakes, two clutches, a gear ring of the P1 planetary row is connected with the B1 brake, a planet carrier is rigidly connected with an input end of the C1 clutch and simultaneously serves as a sun gear of the P2 planetary row; the gear ring of the P2 planetary row is connected with the B2 brake, and the planet carrier is simultaneously connected with the output end of the C1 clutch, the sun gear of the P3 planetary row, the sun gear of the P4 planetary row and the input end of the C2 clutch through splines; the planet carrier of the P3 planet row is connected with the B3 brake, and the gear ring is rigidly connected with the planet carrier of the P4 planet row; the gear ring of the P4 planetary row is connected with the B4 brake, and the planet carrier is connected with the output end of the C2 clutch and the output gear pair.

The loader gearbox in the prior art adopts a plurality of groups of clutches, a plurality of groups of brakes and a plurality of groups of planetary gears to carry out heavy load, light load and gear switching, the gearbox is not tight in transmission path and is structurally auxiliary, energy loss can be generated in the operation process of the gearbox, a large amount of heat is generated, and therefore a cooling device is required to be added for heat dissipation during the whole vehicle design, and the working efficiency is low and the energy loss is large.

Disclosure of Invention

In order to solve the problems of structural assistance and poor heat dissipation of a loader in the prior art, the utility model aims to provide a hydrostatic gearbox which is simpler in structure, more flexible and convenient to control and better in lubricating and heat dissipation capacity.

In order to achieve the above purpose, the present utility model adopts the following technical scheme: the hydrostatic gearbox comprises a box body, a first input part, a second input part, an output part, a box body part and a clutch part, wherein the first input part comprises a first input shaft which is in transmission connection with a first hydraulic motor; the second input component comprises a second input shaft which is in transmission connection with a second hydraulic motor; the clutch component comprises a clutch shaft and a clutch, and the clutch is arranged on the clutch shaft; the output part comprises an output shaft capable of outputting power at two ends; the first input shaft, the second input shaft, the output shaft and the clutch shaft are all rotatably arranged on the box body through bearings; the clutch shaft is in transmission connection with the first input shaft through a clutch, the clutch shaft is in meshed transmission with the output shaft, and the second input shaft is in meshed transmission with the output shaft; the gearbox further comprises a first oil pipe, the first oil pipe supplies oil to a cavity in the clutch shaft through a throttle valve, two ends of the clutch shaft are both arranged on the box body through bearings, a first oil throwing hole is formed in the throttle valve, the first oil throwing hole is positioned between the bearings and the inner wall of the box body, and oil passing through the throttle valve can supply oil to the bearings through the first oil throwing hole; the clutch shaft is also provided with a plurality of second oil throwing holes for throwing oil outwards, the second oil throwing holes extend radially, the second oil throwing holes are communicated with a cavity in the clutch shaft, and the second oil throwing holes supply oil to components arranged on the clutch shaft.

Preferably, the first oil pipe supplies oil to a bearing mounted at the end of the clutch shaft; the gearbox further comprises a second oil pipe which communicates with the interior of the gearbox and supplies oil to another bearing mounted on the clutch shaft.

Preferably, the clutch shaft is fixedly provided with an intermediate gear, the second input shaft is fixedly provided with a second input gear, the output shaft is fixedly provided with an output gear, and the intermediate gear and the second input gear are meshed with the output gear.

Preferably, the first input shaft is provided with an external gear portion protruding therefrom, and the first input shaft is meshed with the transition gear of the clutch through the external gear portion.

Preferably, the box component comprises a left box and a right box, the left box and the right box are fixedly connected, and two ends of the first input shaft, two ends of the second input shaft, two ends of the output shaft and two ends of the clutch shaft are respectively arranged on the left box and the right box.

Preferably, the clutch shaft is mounted on the box body through two tapered roller bearings, the two tapered roller bearings are oppositely arranged, inner rings of the two tapered roller bearings are propped against the clutch shaft, an outer ring of one tapered roller bearing is propped against the inner wall of the box body, and an outer ring of the other tapered roller bearing is propped against the inner wall of the box body through a belleville spring to limit the clutch shaft axially.

Preferably, the clutch comprises a transition gear, a plurality of outer friction plates, a spline seat, a plurality of inner friction plates, a return spring, a baffle plate, a bearing plate, a clutch end cover, a piston and a return spring; the transition gear is rotatably arranged on the clutch shaft, the plurality of outer friction plates are arranged on the transition gear, the spline seat is slidably arranged on the clutch shaft, the plurality of inner friction plates are arranged on the spline seat, the baffle plate is fixedly connected with the clutch shaft, the bearing plate is slidably connected with the clutch shaft, the friction plates are positioned between the baffle plate and the bearing plate, the return spring is arranged between the spline seat and the bearing plate, the return spring endows the bearing plate with a trend of being far away from the friction plates, and the clutch end cover is fixedly connected with the left box body; the clutch end cover is fixedly connected with the connecting part, the piston is located on the inner side of the connecting part, the connecting part and the clutch end cover are in sliding fit with the piston, the piston is rotatably installed on the bearing plate, the connecting part, the clutch end cover and the piston enclose a synthetic oil cavity, an oil inlet communicated with the oil cavity is formed in the connecting part, a reset spring is arranged between the piston and the inner wall of the box, and the reset spring endows the piston with a trend of reducing the size of the oil cavity.

Preferably, the clutch release control device further comprises an operating component, wherein the operating component comprises an electrohydraulic operating valve for controlling the release of the clutch.

Preferably, one end of the output shaft outputs power through the first output flange, the other end of the output shaft is connected with a parking brake, and the parking brake is arranged outside the box body.

Preferably, the power of the first hydraulic motor is greater than the power of the second hydraulic motor.

The technical scheme of the utility model has the beneficial effects that: according to the scheme, power is input through the two hydraulic motors, when one hydraulic motor outputs power, the high-speed walking operation of the loader can be realized, and when the two hydraulic motors output power at the same time, the low-speed heavy-load operation of the loader can be realized; in the scheme, all shafts are supported on the box body part through bearings, and the novel gear box has the characteristics of simple structure, good use reliability, convenience in gear operation and the like; through the oil pipe that communicates the clutch axle can effectually dispel the heat for clutch axle and install the component on the clutch axle, promote the stability of gearbox work.

Drawings

FIG. 1 is a schematic diagram of a transmission;

FIG. 2 is a schematic diagram of a second gearbox configuration;

FIG. 3 is a schematic diagram III of a transmission;

FIG. 4 is a schematic structural view of a transmission fourth;

FIG. 5 is a schematic diagram of the connection structure of the tank and the oil pipe;

FIG. 6 is a schematic view of the mounting structure of an electro-hydraulic operated valve.

Reference numerals: 1. a first input shaft; 2. a first input end cap; 3. a second input shaft; 4. a second input end cap; 5. a second input gear; 6. an output shaft; 7. an output gear; 8. a first output flange; 9. a second output flange; 10. a parking brake; 11. a right box body; 12. a left box body; 13. an oil baffle plate; 14. a pressure switch; 15. an electro-hydraulic operated valve; 16. a clutch shaft; 17. a transition gear; 18. an outer friction plate; 19. an intermediate gear; 20. a spline seat; 21. an inner friction plate; 22. a return spring; 23. a baffle; 24. a pressure bearing plate; 25. a clutch end cap; 26. a cylindrical pin; 27. a piston; 28. a return spring; 29. a retainer ring seat; 30. a retainer ring; 31. a spacer ring; 32. a ninth bearing; 33. a belleville spring; 34. an oil sump; 35. a first oil pipe; 36. an oil storage plug; 37. a heat sink; 38. a second oil pipe; 39. a fifth bearing; 40. a sixth bearing; 41. a tenth bearing; 42. a heat dissipation rib; 43. a throttle valve.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present utility model and should not be construed as limiting the utility model.

In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present 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 configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.

In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present utility model, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.

Examples

1-6, comprising a housing, a first input member, a second input member, an output member, a housing member, and a clutch member, the first input member comprising a first input shaft 1, the first input shaft 1 being in driving connection with a first hydraulic motor; the second input part comprises a second input shaft 3, and the second input shaft 3 is in transmission connection with a second hydraulic motor; the clutch components include a clutch shaft 16 and a clutch mounted on the clutch shaft 16; the output part comprises an output shaft 6 which can output power at two ends; the first input shaft 1, the second input shaft 3, the output shaft 6 and the clutch shaft 16 are all rotatably mounted on the box body through bearings; the clutch shaft 16 is in transmission connection with the first input shaft 1 through a clutch, the clutch shaft 16 is in meshed transmission with the output shaft 6, and the second input shaft 3 is in meshed transmission with the output shaft 6; the gearbox further comprises a first oil pipe 35, the first oil pipe 35 supplies oil to a cavity in the clutch shaft 16 through a throttle valve 43, a first oil throwing hole is formed in the throttle valve 43, and oil passing through the throttle valve 43 can supply oil to a bearing on the clutch shaft through the first oil throwing hole; the clutch shaft 16 is further provided with a plurality of second oil slingers for slinging oil outwards, the second oil slingers extend radially, and the second oil slingers are communicated with the cavity in the clutch shaft 16.

The structure adopts two inputs, and when the machine carries out heavy load work, the two inputs are adopted to drive the gearbox to integrally operate, so that stepless speed change and low-speed heavy load work of the machine are realized; when the machine is in high-speed light load, one of the input shafts inputs power, so that stepless speed change and high-speed walking of the machine are realized; forward and backward movement of the loader are realized by controlling the forward and backward rotation of the two input shafts; and all shafts are supported on the box body part through bearings, so that the novel transmission shaft has the characteristics of simple structure, good use reliability, convenience in gear operation and the like, and can better lubricate and dissipate heat for the transmission shaft and the bearings for supporting the transmission shaft through oil pipes.

In this embodiment, the power of the first hydraulic motor is greater than the power of the second hydraulic motor. The power of the two power sources is different, so that the gearbox can flexibly select a power output mode according to working conditions.

In this embodiment, as shown in fig. 1 and 2, the first oil pipe 35 supplies oil to a bearing mounted on the end of the clutch shaft 16; the gearbox further comprises a second oil pipe 38, which second oil pipe 38 communicates with the interior of the gearbox and supplies oil to another bearing mounted on the clutch shaft 16. By the arrangement, the two bearings with the largest stress on the transmission shaft can be guaranteed to be lubricated and radiated by enough oil, and the running stability and the running sustainability of the gearbox are improved.

As shown in fig. 1 and 2, in the present embodiment, an intermediate gear 19 is fixedly mounted on the clutch shaft 16, a second input gear 5 is fixedly mounted on the second input shaft 3, an output gear 7 is fixedly mounted on the output shaft 6, the intermediate gear 19 and the second input gear 5 are both meshed with the output gear 7, an external gear part protrudes from the first input shaft 1, and the first input shaft 1 is meshed with and driven by a transition gear 17 of the clutch through the external gear part. So set up, the gearbox passes through the gear and carries out the transmission, has guaranteed the stability of gearbox transmission process.

As shown in fig. 1 and 2, in this embodiment, the box body includes a left box body 12 and a right box body 11, concave cavities are respectively provided on the left box body 12 and the right box body 11, the left box body 12 and the right box body 11 are fixedly connected, and a cavity portion of the left box body 12 and a cavity portion of the right box body 11 are buckled to form an inner cavity of the box body. The two ends of the first input shaft 1, the two ends of the second input shaft 3, the two ends of the output shaft 6 and the two ends of the clutch shaft 16 are respectively mounted on the left case 12 and the right case 11 through different bearings.

Further preferably, one end of the first input shaft 1 is connected with the left box body 12 through a first bearing, the other end of the first input shaft 1 is connected with the right box body 11 through a second bearing, a first input end cover 2 is fixed on the right box body 11, and the first input end cover 2 is abutted against an outer ring of the second bearing to axially fix the first input shaft 1. The first hydraulic motor is mounted on the first input end cap 2.

Further preferably, one end of the second input shaft 3 is connected with the left box body 12 through a third bearing, the other end of the second input shaft 3 is connected with the right box body 11 through a fourth bearing, a second input end cover 4 is fixed on the right box body 11, and the second input end cover 4 is abutted against the outer ring of the fourth bearing to axially fix the second input shaft 3. The second hydraulic motor is mounted on the second input end cap 4.

Further preferably, one end of the clutch shaft 16 is connected to the left housing 12 through a fifth bearing 39, and the other end of the clutch shaft 16 is connected to the right housing 11 through a sixth bearing 40. One end of the output shaft 6 is connected to the left case 12 through a seventh bearing, and the other end of the output shaft 6 is connected to the right case 11 through an eighth bearing.

In this embodiment, as shown in fig. 1, both ends of the output shaft 6 extend from the case. Thus, both sides of the gearbox can be driven. Further preferably, a parking brake 10 is fixedly installed on the box body of the gearbox, and the parking brake 10 is connected with one end of the output shaft 6. With this arrangement, when the hydraulic motor power is not input, the parking brake is performed by the parking brake 10.

In this embodiment, as shown in fig. 1, the power input and the power output of the gearbox are both performed on the same side of the box, specifically, the parking brake 10 is mounted on the left box 12, and the first input end cover 2 and the second input end cover 4 are both mounted on the right box 11. By the arrangement, the space required by the gearbox can be smaller, and the arrangement of a machine transmission chain is facilitated.

In this embodiment, as shown in fig. 2, the clutch includes a transition gear 17, a plurality of outer friction plates 18, a spline housing 20, a plurality of inner friction plates 21, a return spring 22, a baffle plate 23, a bearing plate 24, a clutch end cover 25, a piston 27, and a return spring 28; the transition gear 17 is rotatably mounted on the clutch shaft 16, an outer shell part protrudes from the end surface of the transition gear 17, a plurality of outer friction plates 18 are mounted in the outer shell part of the transition gear 17, a spline seat 20 and a plurality of inner friction plates 21 are all located on the inner side of the outer shell part, the spline seat 20 is sleeved and slidably mounted on the clutch shaft 16, a plurality of inner friction plates 21 are mounted on the spline seat 20, a baffle plate 23 is fixedly connected with the clutch shaft 16, a bearing plate 24 is slidably connected with the clutch shaft 16, the friction plates are located between the baffle plate 23 and the bearing plate 24, a return spring 22 is arranged between the spline seat 20 and the bearing plate 24, the return spring 22 gives the bearing plate 24 a trend away from the friction plates, an annular connecting part protrudes from the inner wall of the left box 1, the clutch end cover 25 is fixedly connected with the end part of the connecting part, a piston 27 is located on the inner side of the connecting part, the connecting part and the clutch end cover 25 are slidably matched with the piston 27, the piston 27 is rotatably mounted on the bearing plate 24 through a tenth bearing 41, the connecting part, the clutch end cover 25 and the piston 27 are fixedly connected with the clutch shaft 16, the piston 27 is arranged on the piston end cover 46, an oil inlet 46 is arranged on the connecting part, the piston cavity is communicated with the oil cavity 46, the piston 27 is arranged in the reducing cavity 28, the return spring is arranged in the reducing cavity 46, and the piston 28 is arranged in the reducing cavity 46. The arrangement is such that the various components of the clutch are disposed within the transmission housing. The tenth bearing 41 is a tapered roller bearing, the inner ring of the tenth bearing 41 is tightly fitted with the bearing plate 24, and the outer ring of the tenth bearing 41 is tightly fitted with the piston 27. Further, the return spring 28 is a belleville spring, the return spring 28 is sleeved on the piston 27, a retainer ring seat 29 and a retainer ring 30 are further sleeved on the piston, the retainer ring seat 29 is located between the return spring 28 and the retainer ring 30, and two ends of the retainer ring seat 29 can respectively abut against the return spring 28 and the retainer ring 30.

Further preferably, as shown in fig. 1 and 2, the fifth bearing 39 and the sixth bearing 40 on the clutch shaft 16 are tapered roller bearings, two tapered roller bearings are disposed opposite to each other, inner rings of the two tapered roller bearings are abutted against the clutch shaft 16, an outer ring of one tapered roller bearing is abutted against an inner wall of the left box, and an outer ring of the other tapered roller bearing is abutted against an inner wall of the right box 11 through a disc spring 33, and the disc spring 33 is axially arranged with the clutch shaft 16. By the arrangement, the gap between the clutch shaft 16 and the box body can be automatically adjusted by the force generated by the disc spring 33, and the gap between each bearing arranged on the clutch shaft 16 is adjusted, so that the inner ring and the outer ring of the bearing are always kept in contact, and the separation and the damage of the inner ring and the outer ring of the bearing are avoided.

Further, a cylindrical pin 26 is fixed on the clutch end cover 25, and a positioning hole matched with the cylindrical pin 26 is formed in the piston 27. The cylindrical pin 26 is inserted into the positioning hole and is in sliding fit with the positioning hole. So arranged, the direction of movement of the piston 27 can be ensured. Further, the plurality of cylindrical pins 26 are provided, the plurality of cylindrical pins 26 are arranged around the clutch shaft 16, and the plurality of positioning holes are provided, and the plurality of positioning holes and the plurality of cylindrical pins 26 are in one-to-one correspondence.

Further preferably, the intermediate gear 19 is rotatably mounted on the clutch shaft 16 through two ninth bearings 32, and a part of the second oil slinger on the clutch shaft 16 is located in the middle of the two ninth bearings 32; a portion of the second oil slinger holes on the clutch shaft 16 are located inside the clutch, a portion of the second oil slinger holes are located between the spline housing 20 and the baffle 23, and a portion of the second oil slinger holes are located between the spline housing 20 and the pressure plate 24.

Further preferably, the gearbox further comprises a pressure switch for detecting the pressure value in the oil cavity of the clutch, and the pressure switch determines whether the first input shaft 1 inputs power or not by detecting whether the oil pressure in the oil cavity 46 is lower than a specified value or not, so that slipping and generated heat of the clutch are reduced, and the clutch is protected.

In this embodiment, as shown in fig. 6, the gearbox further includes an operating component, where the operating component includes an electrohydraulic operating valve 15, the electrohydraulic operating valve 15 is installed in the box, and the electrohydraulic operating valve 15 is connected to a hydraulic oil circuit system to control hydraulic oil to enter and exit the oil cavity 46 of the clutch. Furthermore, the hydraulic oil way system is supplied with oil by an external oil pump for working.

The specific control is as follows: when the gearbox outputs coupling power, oil is not filled in a clutch oil cavity 46, an inner friction plate 21 and an outer friction plate 18 of the clutch are connected under the action of a return spring 22 and a return spring 28, the first hydraulic motor is connected with a first input shaft 11, the hydraulic motor drives the first input shaft 1 to rotate, the first input shaft 1 is meshed with a transition gear 17 of the clutch through a first input gear, the transition gear 17 drives a spline seat 20 to rotate through the inner friction plate 21 and the outer friction, the spline seat 20 drives a clutch shaft 16 to rotate, and the clutch shaft 16 rotates through an intermediate gear 19; the second hydraulic motor drives the second input shaft 3 to rotate, the second input shaft 3 drives the second input gear 5 to rotate, the second input gear 5 and the intermediate gear 19 drive the output gear 7 to rotate together, the output gear 7 drives the output shaft 6 to rotate, and the second output flange outputs power and drives the loader to work at a low speed and in a heavy load.

When the gearbox outputs single power, the second hydraulic motor is connected with the second input shaft 3, the second input gear 5 fixedly connected with the second input shaft 3 is meshed with the output gear 7, the operating part injects oil into the oil cavity 46 of the clutch through the electrohydraulic operating valve, so that the return spring 22 and the hydraulic oil drive piston 27 move and compress the return spring 28, the inner friction plate 21 and the outer friction plate 18 of the clutch are separated, the clutch is positioned in a disengaging pile body, the power of the first hydraulic motor cannot be transmitted to the clutch shaft 16, the power of the second hydraulic motor is transmitted to the output shaft 6, and the power of the second hydraulic motor is output through the first output flange and the second output flange on the output shaft 6 and drives the loader to walk at a high speed.

In order to improve the heat dissipation effect, in this embodiment, as shown in fig. 5, an oil collecting plate 44 is disposed above the clutch, the top of the oil collecting plate 44 is provided with an oil collecting groove 34, and the first oil pipe 35 and the second oil pipe 38 are both communicated with the oil collecting groove 34. Specifically, the oil is stored in the box, a part of the structure of the output gear 7 is immersed in the oil stored in the box, the oil in the box is stirred and thrown away when the output gear 7 rotates, the oil thrown away by the gear is collected in the oil collecting groove 34, the oil in the oil collecting groove 34 flows through the first oil pipe 35 and the throttle valve 43 and enters the cavity of the clutch, when the clutch rotates, the oil in the clutch is thrown away from the second oil Kong Feichu, lubrication and heat dissipation are carried out for friction plates and bearings arranged on the clutch, a part of the oil flowing through the throttle valve 43 is discharged from the first oil throwing hole to be lubricated and dissipated for the fifth bearing 39 on the clutch shaft 16, and the second oil pipe 38 supplies oil to the sixth bearing 40 on the clutch shaft 16. By the arrangement, oil liquid used for moistening and radiating in the gearbox can realize self circulation, and meanwhile, a complex structure is not needed.

It is further preferable that, for easy installation, the cavity of the clutch shaft 16 extends radially and penetrates the transmission shaft, two ends of the transmission shaft are respectively provided with an oil storage plug 36 for plugging the cavity, and one end of the throttle valve 43 is communicated with the cavity of the transmission shaft through the oil storage plug 36. By the arrangement, the manufacturing and assembling difficulty of the transmission shaft can be reduced, lubricating oil entering the clutch is stored, and the bearing and the friction plate are fully lubricated.

Further, as shown in fig. 1 to 5, the first oil pipe 35 and the second oil pipe 38 are both installed outside the case, the first oil pipe 35 is installed on the left case 12, and the second oil pipe 38 is installed on the right case 11. So set up, fluid can exchange heat with external environment earlier when oil pipe, improves the radiating efficiency of gearbox.

Further preferably, in order to facilitate the installation of the gearbox, as shown in fig. 5, the oil collecting plate 44 includes a first oil collecting portion and a second oil collecting portion, the first oil collecting portion is fixed on the left box 12, the second oil collecting portion is fixed on the right box 11, and after the left box 12 and the right box 11 are fixedly connected, the first oil collecting portion and the second oil collecting portion are abutted.

In order to facilitate the oil collecting tank 34 to collect oil, in this embodiment, as shown in fig. 5, an inclined oil guide plate 45 is disposed in the tank, the top of the oil guide plate 45 is fixed on the inner wall of the tank, and the bottom of the oil guide plate 45 extends to above the oil collecting tank 34. By this arrangement, the collection efficiency of the oil can be increased, and the members on the clutch shaft 16 can be sufficiently lubricated.

Further preferably, as shown in fig. 5, the oil guide plate 45 includes a first oil guide portion and a second oil guide portion, where the first oil guide portion is fixed on the left case 12, the second oil guide portion is fixed on the right case 11, and the first oil guide portion and the second oil guide portion are abutted after the left case 12 and the right case 11 are fixedly connected. Further preferably, at least one of the oil guide plates 45 is provided.

In order to further improve the lubrication and heat dissipation effects of the oil in the tank, as shown in fig. 1 and 2, in this embodiment, an oil baffle 13 is fixedly installed in the tank, a portion of the oil baffle 13 is immersed in the oil in the tank, the oil baffle 13 is located on a side surface of the output gear 7, and the oil baffle 13 is disposed parallel to the output gear 7. So set up, through setting up baffle 23, the stirring oil mass when output gear 7 rotates is reduced to reduce energy loss and reduce the heat. Further, the oil baffle 13 is mounted on the right case 11.

In order to provide the transmission with sufficient heat dissipation capability, in this embodiment, the power input portion of the transmission is cooled by the cooling fins 37, the power coupling portion of the transmission is cooled by the oil flowing back through the oil pipe, and the power output portion of the transmission is cooled by the oil stored in the transmission. Specifically, as shown in fig. 1 to 5, the first input shaft 1, the second input shaft 3, the output shaft 6 and the clutch shaft 16 are located at different heights, the first input shaft 1 and the second input shaft 3 are located above the output shaft 6, the cooling fin 37 is mounted on the box body, the cooling fin 37 is mounted at a position close to the end of the first input shaft 1 and the end of the second input shaft 3, the clutch shaft 16 is provided with a cavity, and the first oil pipe 35 and the second oil pipe 38 supply oil to the two ends of the clutch shaft 16 respectively. Further said fins 37 are provided in plurality. This arrangement allows the first input shaft 1, the second input shaft 3, the clutch shaft 16 and the output shaft 6 in the gearbox to be lubricated and cooled effectively.

In this embodiment, in order to further improve the heat dissipation effect of the gearbox, as shown in fig. 3 and fig. 4, the outer surface of the box body is protruded with heat dissipation ribs 42 that are criss-cross. So set up, increase the area of contact of box and air, and then further improve the radiating efficiency of gearbox.

In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

Although embodiments of the present utility model have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the utility model, and that variations, modifications, alternatives, and variations may be made in the above embodiments by those skilled in the art without departing from the spirit and principles of the utility model.

Claims (10)

1. A hydrostatic transmission, characterized by: comprises a box body, a first input part, a second input part, an output part, a box body part and a clutch part,

the first input part comprises a first input shaft (1), and the first input shaft (1) is in transmission connection with the first hydraulic motor; the second input part comprises a second input shaft (3), and the second input shaft (3) is in transmission connection with a second hydraulic motor; the clutch component comprises a clutch shaft (16) and a clutch, wherein the clutch is arranged on the clutch shaft (16); the output part comprises an output shaft (6) capable of outputting power at two ends;

the first input shaft (1), the second input shaft (3), the output shaft (6) and the clutch shaft (16) are rotatably arranged on the box body through bearings;

the clutch shaft (16) is in transmission connection with the first input shaft (1) through a clutch, the clutch shaft (16) is in meshed transmission with the output shaft (6), and the second input shaft (3) is in meshed transmission with the output shaft (6);

the gearbox further comprises a first oil pipe (35), the first oil pipe (35) supplies oil to a cavity in the clutch shaft (16) through a throttle valve (43), two ends of the clutch shaft (16) are arranged on the gearbox body through bearings, a first oil throwing hole is formed in the throttle valve (43), the first oil throwing hole is formed between the bearings and the inner wall of the gearbox body, and oil passing through the throttle valve (43) can supply oil to the bearings through the first oil throwing hole; the clutch shaft (16) is also provided with a plurality of second oil throwing holes for throwing oil outwards, the second oil throwing holes extend radially, the second oil throwing holes are communicated with a cavity in the clutch shaft (16), and the second oil throwing holes supply oil to components arranged on the clutch shaft (16).

2. A hydrostatic transmission as set forth in claim 1, wherein: the first oil pipe (35) supplies oil to a bearing arranged at the end part of the clutch shaft (16); the gearbox further comprises a second oil pipe (38), which second oil pipe (38) communicates with the interior of the gearbox and supplies oil to another bearing mounted on the clutch shaft (16).

3. A hydrostatic transmission as set forth in claim 1, wherein: an intermediate gear (19) is fixedly arranged on the clutch shaft (16), a second input gear (5) is fixedly arranged on the second input shaft (3), an output gear (7) is fixedly arranged on the output shaft (6), and the intermediate gear (19) and the second input gear (5) are both meshed with the output gear (7).

4. A hydrostatic transmission as set forth in claim 1, wherein: an external gear part is protruded on the first input shaft (1), and the first input shaft (1) is meshed and driven with a transition gear (17) of the clutch through the external gear part.

5. A hydrostatic transmission as set forth in claim 1, wherein: the box body part comprises a left box body (12) and a right box body (11), wherein the left box body (12) is fixedly connected with the right box body (11), and two ends of the first input shaft (1), two ends of the second input shaft (3), two ends of the output shaft (6) and two ends of the clutch shaft (16) are respectively arranged on the left box body (12) and the right box body (11).

6. A hydrostatic transmission as set forth in claim 1, wherein: the clutch shaft (16) is arranged on the box body through two tapered roller bearings, the two tapered roller bearings are oppositely arranged, inner rings of the two tapered roller bearings are propped against the clutch shaft (16), the outer ring of one tapered roller bearing is propped against the inner wall of the box body, and the outer ring of the other tapered roller bearing is propped against the inner wall of the box body through a belleville spring (33) to axially limit the clutch shaft (16).

7. A hydrostatic transmission as set forth in claim 1, wherein: the clutch comprises a transition gear (17), a plurality of outer friction plates (18), a spline seat (20), a plurality of inner friction plates (21), a return spring (22), a baffle plate (23), a bearing plate (24), a clutch end cover (25), a piston (27) and a return spring (28);

the transition gear (17) is rotatably arranged on the clutch shaft (16), a plurality of outer friction plates (18) are arranged on the transition gear (17), a spline seat (20) is slidably arranged on the clutch shaft (16), a plurality of inner friction plates (21) are arranged on the spline seat (20), a baffle plate (23) is fixedly connected with the clutch shaft (16), a bearing plate (24) is slidably connected with the clutch shaft (16), the friction plates are arranged between the baffle plate (23) and the bearing plate (24), a return spring (22) is arranged between the spline seat (20) and the bearing plate (24), the return spring (22) endows the bearing plate (24) with a trend of being far away from the friction plates, and a clutch end cover (25) is fixedly connected with the left box body (12);

the clutch end cover (25) is fixedly connected with the connecting portion, the piston (27) is located on the inner side of the connecting portion, the connecting portion and the clutch end cover (25) are in sliding fit with the piston (27), the piston (27) is rotatably mounted on the bearing plate (24), the connecting portion, the clutch end cover (25) and the piston (27) enclose a synthetic oil cavity, an oil inlet communicated with the oil cavity is formed in the connecting portion, a return spring (28) is arranged between the piston (27) and the inner wall of the box, and the return spring (28) gives the piston (27) a trend of reducing the size of the oil cavity.

8. A hydrostatic transmission as set forth in claim 1, wherein: the clutch release control device also comprises an operating component, wherein the operating component comprises an electrohydraulic operating valve (15) for controlling the release of the clutch.

9. A hydrostatic transmission as set forth in claim 1, wherein: one end of the output shaft (6) outputs power through the first output flange (8), the other end of the output shaft (6) is connected with the parking brake (10), and the parking brake (10) is arranged outside the box body.

10. A hydrostatic transmission as set forth in claim 1, wherein: the power of the first hydraulic motor is greater than the power of the second hydraulic motor.