A multifunctional hydraulic transmission braking system

Abstract

The multifunctional hydraulic transmission brake system disclosed in the present invention includes a hydraulic valve group, a hydraulic motor, a hydraulic clutch, a planetary reducer and a hydraulic brake assembly. The motor housing of the hydraulic motor extends toward one side of its output shaft to form a hollow spline transmission shaft. The high-speed end brake and the hydraulic clutch are both integrated inside the spline transmission shaft. The end of the hydraulic clutch away from the hydraulic motor is connected to the planetary reducer, making the overall structure very compact and small in size. At the same time, since the housings of the high-speed end brake, the hydraulic motor and the hydraulic clutch are an integrated structure (spline transmission shaft), the system has good rigidity and high reliability. On the other hand, the inner ring gear of the planetary reducer extends toward the side of the hydraulic motor to the outside of the spline transmission shaft. A low-speed end brake is provided between the inner ring gear extension section and the spline transmission shaft, thereby realizing a double-insurance braking function, effectively solving the problems of the existing hydraulic transmission brake device with complex structure, low integration and single function.

Description

Technical Field

[0001] The present invention relates to the field of hydraulic drive technology, in particular to a highly integrated multifunctional hydraulic transmission brake system. Background Art

[0002] Existing hydraulic brake systems often have low integration levels and single functions. In practice, they often require multiple components to perform multiple functions. This results in complex structures, large size and weight, high costs, and low reliability. For example, when used on a conventional hydraulic winch, achieving free lowering requires a clutch mechanism inside or at the end of the drum. This design not only increases the winch's size, length, and weight, but also creates complexity and high costs. Summary of the Invention

[0003] The purpose of the present invention is to provide a multifunctional hydraulic transmission braking system which has the functions of a clutch and a brake, and has high integration, compact structure and high reliability, and can solve the problems of the above-mentioned prior art such as complex device structure, low integration and single function.

[0004] To achieve the above object, the present invention provides the following solutions:

[0005] The present invention provides a multifunctional hydraulic transmission brake system, comprising:

[0006] A hydraulic motor comprising an output shaft, a rotor, and a motor housing, wherein the rotor is sleeved on the output shaft, and the motor housing extends toward the power output direction of the output shaft to form a hollow spline transmission shaft;

[0007] a hydraulic clutch, the hydraulic clutch being located in the spline transmission shaft and one end of the hydraulic clutch being connected to the output shaft;

[0008] a planetary reducer, the planetary reducer being connected to the other end of the hydraulic clutch via an intermediate shaft, the planetary carrier of the planetary reducer being supported on and connected to the spline transmission shaft; the inner ring gear of the planetary reducer extending toward the end close to the hydraulic motor to the outside of the spline transmission shaft, forming an inner ring gear extension section;

[0009] a hydraulic brake assembly, the hydraulic brake assembly comprising a high-speed end brake and a low-speed end brake, the high-speed end brake being disposed between the motor housing and the rotor, and the low-speed end brake being disposed between the inner gear ring extension and the spline transmission shaft;

[0010] A hydraulic valve group is connected to the hydraulic motor and the hydraulic clutch.

[0011] Optionally, the intermediate shaft includes:

[0012] a front axle, on which the planetary reducer is mounted;

[0013] A rear axle, one end of which is connected to the hydraulic clutch, and the other end of which is connected to an end of the front axle close to the hydraulic clutch through a spline sleeve.

[0014] Optionally, the rear axle and the spline sleeve are both located inside the spline transmission shaft, and a support ring is provided between the outer ring of the spline sleeve and the inner wall of the spline transmission shaft; wherein, the outer periphery of the support ring is fixed on the inner wall of the spline transmission shaft, and a ball bearing is provided between the inner periphery of the support ring and the outer ring of the spline sleeve.

[0015] Optionally, the hydraulic clutch is a multi-disc hydraulically controlled normally closed structure, which includes:

[0016] a sleeve, one end of which is fixedly connected to the output shaft, and an inner wall of the sleeve is provided with a plurality of first fixed friction plates;

[0017] A pressure block, the pressure block is located in the sleeve, the pressure block is fixedly sleeved on the intermediate shaft, a plurality of first dynamic friction plates are provided on the outer periphery of the pressure block, and the plurality of first dynamic friction plates and the plurality of first fixed friction plates are alternately arranged;

[0018] An I-shaped piston, the I-shaped piston being arranged at one end of the pressure block away from the output shaft, and the I-shaped piston being sleeved on the intermediate shaft;

[0019] A top block is arranged between the outer ring recess of the I-shaped piston and the inner wall of the spline transmission shaft, a compression spring is arranged between the end of the outer ring recess of the I-shaped piston close to the output shaft and the top block, and a first oil chamber is arranged between the end of the outer ring recess of the I-shaped piston away from the output shaft and the top block; the first oil chamber is connected to the hydraulic valve group.

[0020] Optionally, the high-speed end brake is a multi-disc hydraulically controlled normally closed structure, which includes:

[0021] a second dynamic friction plate, wherein the second dynamic friction plate is disposed on the inner wall of the motor housing, and a plurality of the second dynamic friction plates are disposed along the axial direction of the motor housing;

[0022] a second fixed friction plate, the second fixed friction plate being disposed on the rotor, and a plurality of the second fixed friction plates being disposed along the axial direction of the motor housing, the plurality of the second fixed friction plates and the plurality of the second movable friction plates being arranged alternately;

[0023] A cylindrical piston, wherein the cylindrical piston ring is sleeved between the inner wall of the motor housing and the rotor; a cover plate is provided at the end of the motor housing away from the hydraulic clutch, a compression spring is provided between the end of the cylindrical piston close to the cover plate and the cover plate, and a second oil chamber is provided between the cylindrical piston and the inner wall of the spline transmission shaft; the second oil chamber is connected to the hydraulic valve group.

[0024] Optionally, the low-speed end brake is a multi-disc hydraulically controlled normally closed structure, which includes:

[0025] a third dynamic friction plate, the third dynamic friction plate being arranged on the outer periphery of one end of the spline transmission shaft close to the planetary reducer, and a plurality of the third dynamic friction plates being arranged along the axial direction of the spline transmission shaft;

[0026] a third fixed friction plate, the third fixed friction plate being arranged on the inner wall of the inner gear ring extension section, and a plurality of the third fixed friction plates being arranged along the axial direction of the inner gear ring extension section, the plurality of the third fixed friction plates and the plurality of the third dynamic friction plates being arranged alternately;

[0027] An annular piston, the annular piston ring is sleeved between the outer wall of the spline transmission shaft and the inner wall of the rear cover, and the rear cover is connected to the end of the inner ring extension section away from the planetary reducer; a compression spring is provided between the annular piston and the inner wall of the rear cover, and a third oil chamber is provided between the annular piston and the outer wall of the spline transmission shaft, and the third oil chamber is connected to the hydraulic valve group.

[0028] Optionally, the hydraulic motor is a swash plate plunger hydraulic motor.

[0029] Optionally, the planetary reducer is a three-stage planetary reducer, which includes:

[0030] A first-stage reduction mechanism, comprising a first-stage sun gear, a first-stage planetary gear, and a first-stage planetary carrier. The first-stage sun gear is disposed at an end of the intermediate shaft away from the hydraulic clutch, and a plurality of first-stage planetary gears are meshed on the outer periphery of the first-stage sun gear. The plurality of first-stage planetary gears are rotatably mounted on the first-stage planetary carrier. The end of the inner gear ring O away from the hydraulic motor is connected to a front cover, and any of the first-stage planetary gears is meshed with the inner wall of the front cover.

[0031] A two-stage reduction mechanism, comprising a two-stage center gear, two-stage planetary gears, and a two-stage planetary carrier. The two-stage center gear is sleeved on the outer periphery of the intermediate shaft but is not connected to the intermediate shaft. The one-stage planetary carrier is sleeved on the two-stage center gear and is key-connected to the two-stage center gear. A plurality of the two-stage planetary gears are meshed with the outer periphery of the two-stage center gear. The plurality of the two-stage planetary gears are rotatably mounted on the two-stage planetary carrier, and any one of the two-stage planetary gears is meshed with the inner wall of the inner gear ring extension section.

[0032] A three-stage reduction mechanism includes a three-stage center wheel, three-stage planetary wheels and a three-stage planetary carrier. The three-stage center wheel is sleeved on the outer periphery of the intermediate shaft but is not connected to the intermediate shaft. The two-stage planetary carrier is sleeved on the three-stage center wheel and is key-connected to the three-stage center wheel. Several three-stage planetary wheels are meshed with the outer periphery of the three-stage center wheel. Several three-stage planetary wheels are rotatably mounted on the three-stage planetary carrier, and any one of the three-stage planetary wheels is meshed with the inner wall of the inner gear ring extension section. The three-stage planetary carrier is key-connected to the spline transmission shaft.

[0033] The two-stage reduction mechanism is located between the one-stage reduction mechanism and the hydraulic clutch, and the three-stage reduction mechanism is located between the two-stage reduction mechanism and the hydraulic clutch.

[0034] Optionally, an involute internal spline is formed on the three-stage planetary carrier, and an involute external spline is provided on the outer wall of the spline transmission shaft at one end away from the pressure motor. The three-stage planetary carrier and the end of the spline transmission shaft away from the pressure motor are floatingly connected via the involute spline.

[0035] Optionally, a spline section for fixing the multifunctional hydraulic transmission braking system is provided at one end of the spline transmission shaft away from the planetary reducer, and the outer wall of the inner ring extension section is ringed with a flange, and a plurality of fixing holes are provided on the flange at intervals along its circumference.

[0036] Compared with the prior art, the present invention has achieved the following technical effects:

[0037] The present invention discloses a highly integrated multifunctional hydraulic transmission brake system, in which the motor housing of the hydraulic motor extends toward one side of its output shaft to form a hollow spline transmission shaft, and the high-speed end brake and the hydraulic clutch are both integrated inside the spline transmission shaft, that is, the inner hole of the spline transmission shaft is both the housing of the high-speed end brake and the hydraulic motor, and the housing of the hydraulic clutch; the end of the hydraulic clutch away from the hydraulic motor is connected to the planetary reducer, and the spline transmission shaft also constitutes the support shaft of the planetary carrier of the planetary reducer, making the overall structure very compact and small in size; at the same time, because the housings of the high-speed end brake, the hydraulic motor and the hydraulic clutch are an integrated structure (spline transmission shaft), the system has good rigidity and high reliability. When in use, the motor housing of the hydraulic motor (including the spline transmission shaft) is used as the fixed end, and the inner gear ring of the planetary reducer (the housing of the low-speed end brake) is used as the power output end. It can be used for wheel-side drive reducers of various vehicles, thereby simplifying the structure and integrating the drive, braking and clutch into one. In addition, when the clutch is used in this embodiment, it can be used for a mooring winch, and when the clutch is in a normally closed state, it can be used for a safe manned lifting winch. The multifunctional hydraulic transmission brake system of this embodiment integrates the hydraulic motor, clutch, high-speed end brake and low-speed end brake into one, and can be hidden in the winch drum. Therefore, it has the characteristics of compact structure, small size, light weight and reliable safety.

[0038] On the other hand, in the multifunctional hydraulic transmission braking system of the present invention, the inner ring gear of the planetary reducer extends toward the hydraulic motor side to the outside of the spline transmission shaft, and a low-speed end brake is provided between the formed inner ring gear extension section and the spline transmission shaft (that is, the housing of the low-speed end brake and the inner ring gear are an integrated structure), thereby realizing a double insurance braking function. It not only effectively solves the problem that the hydraulic transmission braking device in the prior art has a low degree of integration, and in actual application usually requires a combination of multiple components to complete multiple functions, so the structure is complex, the volume and weight are large, the cost is high, and the reliability is low, but also solves the problem that the existing clutch brake integrated hydraulic transmission device lacks a low-speed end braking mechanism and has a single function. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0040] Figure 1 This is a schematic structural diagram of a multifunctional hydraulic transmission brake system disclosed in an embodiment of the present invention;

[0041] Figure 2 This is a schematic structural diagram of the planetary reducer disclosed in an embodiment of the present invention.

[0042] Among them, the accompanying drawings are marked as follows: 1. hydraulic valve group; 2. hydraulic motor; 3. hydraulic clutch; 4. planetary reducer; 5. output shaft; 6. splined drive shaft; 7. high-speed end brake; 8. low-speed end brake; 9. rotor; 10. inner ring gear; 11. inner ring gear extension section; 12. first-stage sun gear; 13. third-stage planetary carrier; 14. front axle; 15. rear axle; 16. splined sleeve; 17. front cover; 18. first-stage planetary gear; 19. support ring; 20. sleeve; 21. pressure block; 22. I-shaped piston; 23. top block; 24. compression spring; 25. cylindrical piston; 26. cover plate; 27. rear cover; 28. annular piston; 29. ​​splined section; 30. fixing hole; 31. third-stage center wheel; 32. third-stage planetary gear; 33. second-stage center wheel; 34. second-stage planetary carrier; 35. second-stage planetary gear; 36. first-stage planetary carrier. DETAILED DESCRIPTION

[0043] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0044] One of the purposes of the present invention is to provide a multifunctional hydraulic transmission braking system that has the functions of a clutch and a brake, and has high integration, compact structure, and high reliability, and can solve the problems of complex device structure, low integration and single function in the prior art.

[0045] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0046] Example 1

[0047] like Figure 1 As shown, this embodiment provides a highly integrated multifunctional hydraulic transmission brake device, which mainly includes a hydraulic valve group 1, a hydraulic motor 2, a hydraulic clutch 3, a planetary reducer 4 and a hydraulic brake assembly. The output shaft 5 of the hydraulic motor 2 is connected to one end of the hydraulic clutch 3. The motor housing of the hydraulic motor 2 extends toward the end close to the output shaft 5 to form a hollow spline transmission shaft 6. The hydraulic clutch 3 is arranged in the spline transmission shaft 6. The other end of the hydraulic clutch 3 is connected to the planetary reducer 4 through an intermediate shaft. The planetary carrier of the planetary reducer 4 is supported on the spline transmission shaft 6 and is floatingly connected to the spline transmission shaft 6. The end of the inner ring 10 of the planetary reducer 4 close to the hydraulic motor 2 extends toward the direction close to the hydraulic motor 2 to the outside of the spline transmission shaft 6 to form an inner ring extension section 11, as shown in FIG. Figure 1 From the perspective shown, the right end of the splined drive shaft 6 is sheathed within the left end of the inner ring gear extension 11. The hydraulic brake assembly includes a high-speed brake 7 and a low-speed brake 8. The high-speed brake 7 is located between the motor housing and the motor rotor 9, while the low-speed brake 8 is located between the inner ring gear extension 11 of the planetary reducer 4 and the splined drive shaft 6.

[0048] Preferably, the planetary reducer 4 of this embodiment is a multi-stage planetary reducer. The front end (the end away from the hydraulic motor 2) of the inner ring gear 10 of the multi-stage planetary reducer is connected to a front cover 17. The first-stage inner ring gear of the multi-stage planetary reducer is disposed on the inner wall of the front cover 17. The first-stage planetary gears 18 of the multi-stage planetary reducer mesh with the first-stage inner ring gear on the front cover 17. The front cover 17 is used to enclose the front end (the end away from the hydraulic motor 2) of the multi-functional hydraulic transmission brake device. The placement of the first-stage inner ring gear of the multi-stage planetary reducer on the inner wall of the front cover 17 fully utilizes the space inside the front cover 17.

[0049] In this embodiment, the end of the intermediate shaft away from the hydraulic clutch 3 constitutes the first-stage sun gear 12 of the multi-stage planetary reducer, and the third-stage planet carrier 13 of the multi-stage planetary reducer is located at the rear end of the first-stage sun gear 12 ( Figure 1 The intermediate shaft includes a front shaft 14 and a rear shaft 15 arranged coaxially and arranged in accordance with Figure 1 The perspectives shown are placed from right to left, with the left end of the front axle 14 ( Figure 1 The left end of the perspective shown) and the right end of the rear axle 15 ( Figure 1 The right end of the perspective shown) is connected by a spline sleeve 16, and the left end of the rear axle 15 ( Figure 1 The left end of the perspective shown) is connected to the hydraulic clutch 3, and the first-stage sun gear 12 is set at the right end of the front shaft 14 ( Figure 1 The embodiment arranges the three-stage planet carrier 13 of the multi-stage planetary reducer at the rear side of the first-stage sun gear 12 ( Figure 1 The left side of the illustrated perspective (i.e., the third-stage planetary carrier 13) is located between the hydraulic clutch 3 and the first-stage sun gear 12. This facilitates shortening the device, improving the rigidity of the transmission system, and reducing its size. Furthermore, a support ring 19 is provided between the splined sleeve 16 and the inner wall of the splined transmission shaft 6. The outer periphery of the support ring 19 is fixed to the inner wall of the splined transmission shaft 6, and a ball bearing is provided between the inner periphery (inner ring) of the support ring 19 and the outer wall of the splined sleeve 16, forming a rotational connection.

[0050] As a preferred embodiment, the multi-stage planetary reducer of this embodiment preferably adopts a three-stage planetary gear mechanism, such as Figure 2As shown, it mainly includes a primary sun gear 12, a third-stage planetary carrier 13, a third-stage center gear 31, third-stage planetary gears 32, a second-stage center gear 33, a second-stage planetary carrier 34, second-stage planetary gears 35, a primary planetary carrier 36, and a primary planetary gear 18. The end of the intermediate shaft away from the hydraulic clutch 3 constitutes the primary sun gear 12 (or primary center gear) of the three-stage planetary gear mechanism, and the third-stage planetary carrier 13 of the three-stage planetary gear mechanism is located at the rear side of the primary sun gear 12. The outer periphery of the first-stage sun gear 12 is meshed with a plurality of first-stage planetary gears 18, which are all mounted on a first-stage planetary carrier 36. Any first-stage planetary gear 18 is meshed with the inner ring of the front cover 17. The second-stage center gear 33 is sleeved on the outer periphery of the above-mentioned intermediate shaft but is not connected to the above-mentioned intermediate shaft. The first-stage planetary carrier 36 is sleeved on the second-stage center gear 33 and is key-connected to the second-stage center gear 33. The outer periphery of the second-stage center gear 33 is meshed with a plurality of second-stage planetary gears 35, and any second-stage planetary gear 35 is meshed with the inner wall of the inner gear ring extension section 11. Several secondary planetary gears 35 are mounted on the secondary planetary carrier 34; the tertiary center gear 31 is sleeved on the outer periphery of the above-mentioned intermediate shaft, but is not connected to the above-mentioned intermediate shaft. The secondary planetary carrier 34 is sleeved on the tertiary center gear 31 and is keyed to the tertiary center gear 31. Several tertiary planetary gears 32 are meshed with the outer periphery of the tertiary center gear 31. Any tertiary planetary gear 32 is meshed with the inner wall of the inner gear ring extension section 11. Several secondary planetary gears 35 are mounted on the tertiary planetary carrier 13, and the tertiary planetary carrier 13 is splined to the spline transmission shaft 6. The above-mentioned primary planetary carrier 36, secondary planetary carrier 34 and tertiary planetary carrier 13 are all sleeved on the outer periphery of the above-mentioned intermediate shaft, but are not connected to the above-mentioned intermediate shaft. Figure 2 As shown, the primary reduction mechanism is composed of the primary sun gear 12, the primary planetary gear 18, and the primary planetary carrier 36, the secondary reduction mechanism is composed of the secondary center gear 33, the secondary planetary gear 35, and the secondary planetary carrier 34, and the tertiary reduction mechanism is composed of the tertiary center gear 31, the tertiary planetary gear 32, and the tertiary planetary carrier 13. Figure 2 right end shown) forward ( Figure 2 The left end shown) are arranged in sequence with a compact structure.

[0051] When the three-stage planetary gear mechanism described above is in operation, the output shaft 5 of the hydraulic motor 2 drives the primary sun gear 12 to rotate via the hydraulic clutch 3, the rear shaft 15, and the splined sleeve 16. The primary sun gear 12 drives the primary planet gears 18 to rotate. The rotation of the primary planet gears 18 drives the primary reducer housing (i.e., the front cover 17). The revolution of the primary planet gears 18 (rotating along with the output shaft 5 along with the primary sun gear 12) drives the primary planet carrier 36 to rotate. The primary planet carrier 36 drives the secondary sun gear 33 to rotate. The secondary sun gear 33 drives the secondary planet gears 35 to rotate. The rotation of the secondary planet gears 35 drives the reducer housing (i.e., the inner ring gear extension 11). The revolution of the secondary planet gears 35 drives the secondary planet carrier 34 to rotate. The secondary planet carrier 34 rotates the tertiary center gear 31, which in turn rotates the tertiary planetary gears 32. The rotation of the tertiary planetary gears 32 rotates the reducer housing (i.e., the inner ring gear extension 11). The tertiary planetary gears 32 do not revolve. This is because the tertiary planet carrier 13 and the spline drive shaft 6 are splined and fixed, so the tertiary planet carrier 13 also does not move. In summary, this three-stage planetary gear mechanism is a shell-rotating planetary reducer. The inner ring gear 10 and the inner ring gear extension 11 are located on the outer ring of the three-stage planetary gear mechanism, forming the reducer housing. This three-stage planetary gear mechanism is powered by the hydraulic motor 2, with the reducer housing (i.e., the inner ring gear 10 and the inner ring gear extension 11) as the output. The reducer housing (i.e., the inner ring gear 10 and the inner ring gear extension 11) and the front cover 17 are connected by screws and rotate together.

[0052] In this embodiment, the hydraulic clutch 3 is a multi-disc hydraulically controlled normally closed structure, which includes a sleeve 20 and a pressure block 21. One end of the sleeve 20 is fixedly connected to the output shaft 5 of the hydraulic motor 2 via a spline, and a plurality of first fixed friction plates are provided in the sleeve 20; the center of the pressure block 21 is connected to the aforementioned intermediate shaft via a spline, and the outer periphery of the pressure block 21 is provided with a corresponding plurality of dynamic friction plates, and the plurality of first dynamic friction plates and the plurality of first fixed friction plates are arranged alternately. An I-shaped piston 22 is provided on the front side of the pressure block 21 (i.e., the side of the pressure block 21 away from the output shaft 5), and a top block 23 is provided between the middle part of the I-shaped piston 22 (i.e., the inner concave part of the outer wall) and the inner wall of the spline transmission shaft 6. The rear end of the I-shaped piston 22 (i.e., Figure 1 The front side (left end of the viewing angle shown) Figure 1 A compression spring 24 is provided between the top block 23 and the front end of the I-shaped piston 22 ( Figure 1 The rear side (right end of the perspective shown) Figure 1A first oil chamber is provided between the upper block 22 and the top block 22, and the first oil chamber is connected to the hydraulic valve assembly 1 via a hydraulic oil circuit. When the oil inlet pressure of the first oil chamber of the hydraulic clutch 3 increases, the I-shaped piston 22 is pushed to overcome the elastic force of the compression spring 24 and move toward the hydraulic motor 2, causing the first dynamic friction plate to disengage from the first fixed friction plate, and the hydraulic clutch 3 is in a disengaged state. When the first oil chamber loses pressure, the I-shaped piston 22 moves toward the planetary reducer 4 under the elastic force (reset) of the compression spring 24, causing the first dynamic friction plate to fit the first fixed friction plate, and the hydraulic clutch 3 is in a closed state. As a preferred embodiment, the opening and closing of the hydraulic clutch 3 can be manually operated. For example, when used on a winch, the operating handle is provided with an anti-misoperation mechanism (existing technology). To operate the handle, two movements are required, thus avoiding the risk of misoperation when lifting the winch.

[0053] In this embodiment, the high-speed end brake 7 is preferably a multi-disc, hydraulically controlled, normally closed structure. It includes multiple second dynamic friction plates mounted on the inner wall of the motor housing and several second fixed friction plates mounted on the rotor 9. These plates are arranged in an alternating pattern. A cylindrical piston 25 is sleeved between the inner wall of the motor housing and the rotor 9. A compression spring 24 is provided between the cylindrical piston 25 and the cover plate 26 on the left side of the hydraulic motor 2. A second oil chamber is provided between the cylindrical piston 25 and the splined drive shaft 26. This second oil chamber is connected to the hydraulic valve assembly 1 via a hydraulic oil circuit. When the oil pressure in the second oil chamber of the high-speed end brake 7 increases, the cylindrical piston 25 is pushed toward the hydraulic valve assembly 1, overcoming the elastic force of the compression spring 24. The second dynamic friction plate disengages the second fixed friction plate, and the high-speed end brake 7 enters the disengaged state. When the second oil chamber loses pressure, the cylindrical piston 25, under the elastic force (reset) of the compression spring 24, moves toward the hydraulic clutch 3, causing the second dynamic friction plate to engage the first fixed friction plate. The high-speed end brake 7 enters the closed state, locking the rotor 9 of the hydraulic motor 2. The high-speed end brake 7 of this embodiment has a large braking force and is hydraulically controlled to automatically open and close in response to the start and stop of the hydraulic motor 2, eliminating the need for manual operation. Traditional band brakes, due to their high opening pressure and large travel, cannot automatically open and close, and therefore lack the automatic emergency braking function in the event of a component failure in the system. However, the high-speed end brake 7 of this embodiment, due to its multi-disc, hydraulically controlled, normally closed structure, has an automatic emergency braking function, making it suitable for safe manned hoist winches.

[0054] In this embodiment, the low-speed end brake 8 is preferably a multi-disc hydraulically controlled normally closed structure, which includes a plurality of third dynamic friction plates arranged on the outer periphery of the spline transmission shaft 6 and a plurality of third fixed friction plates arranged on the inner wall of the inner ring gear extension section 11. The rear side of the inner ring gear extension section 11 ( Figure 1 The left side of the perspective shown) is connected to the rear cover 27, and the two ends of the rear cover 27 are respectively connected to the rear side of the inner gear ring extension section 11 ( Figure 1The rear cover 27 is connected to the outer wall of the spline drive shaft 6 (left side of the perspective shown), sealing the interior of the inner ring gear extension 11. An annular piston 28 is installed between the inner wall of the rear cover 27 and the outer periphery of the spline drive shaft 6. A compression spring 24 is installed between the end of the annular piston 28 closest to the hydraulic motor 2 and the rear cover 27. A third oil chamber is located between the end of the annular piston 28 facing away from the hydraulic motor 2 and the spline drive shaft 26. This third oil chamber is connected to the hydraulic valve assembly 1 via a hydraulic oil circuit. When the oil inlet pressure of this third oil chamber of the low-speed end brake 8 increases, the annular piston 28 is pushed toward the hydraulic motor 2, overcoming the elastic force of the compression spring 25. The third dynamic friction plate disengages the third fixed friction plate, and the low-speed end brake 8 enters the disengaged state. When the third oil chamber loses pressure, the annular piston 28, under the elastic force (reset) of the compression spring 24, moves toward the planetary reducer 4, causing the third dynamic friction plate to engage with the third fixed friction plate, and the low-speed end brake 8 enters the engaged state. The low-speed end brake 8 of this embodiment can achieve a dynamic braking force greater than 1.1 times the rated load force and a static braking force greater than 1.5 times the rated load force, which meets the technical requirements specified by LR (Lloyd's Register).

[0055] In this embodiment, the hydraulic motor 2 is preferably a swash plate plunger hydraulic motor, which has a dual-speed function, low speed for heavy loads and medium-high speed for light loads.

[0056] In this embodiment, the three-stage planetary carrier 13 of the multi-stage planetary reducer is formed with an involute internal spline, and the front end of the spline transmission shaft 6 ( Figure 1 The outer periphery of the planetary reducer 3 (right end, as viewed from the right side of the diagram) is provided with involute external splines, which enable a floating connection between the three-stage planet carrier 13 and the splined transmission shaft 6. When the planetary reducer 3 employs a multi-stage structure, the floating connection between the three-stage planet carrier 13 and the splined transmission shaft 6 via the involute splines ensures balanced force distribution across each stage of the planetary mechanism, preventing damage to the planetary reducer or shortening its service life due to excessive force on any one stage.

[0057] In this embodiment, the rear end of the spline transmission shaft 6 ( Figure 1 The left end of the viewing angle shown is provided with a spline section 29 for securing the multifunctional hydraulic transmission brake system to the frame. A flange is provided on the outer periphery of the inner ring gear extension 11, and the flange is provided with multiple fixing holes 30. The spline section is used to secure the multifunctional hydraulic transmission brake system of this embodiment to the frame as a whole, while the multiple fixing holes 30 in the flange are used for connecting to other mechanisms to output power.

[0058] In this embodiment, the motor housing of the hydraulic motor 2 extends toward one side of its output shaft 5 to form a hollow spline transmission shaft 6, and the high-speed end brake 7 and the hydraulic clutch 3 are both integrated inside the spline transmission shaft 6, that is, the inner hole of the spline transmission shaft 6 is both the housing of the high-speed end brake 7 and the hydraulic motor 2, and the housing of the hydraulic clutch 3; the front end of the hydraulic clutch 3, that is, the end away from the hydraulic motor 2 is connected to the planetary reducer 4, and the spline transmission shaft 6 also constitutes the support shaft of the planetary carrier of the planetary reducer 4, so that the overall structure is very compact and small in size; at the same time, since the housings of the high-speed end brake 7, the hydraulic motor 2 and the hydraulic clutch 3 are an integrated structure (spline transmission shaft 6), the system has good rigidity and high reliability. Furthermore, the planetary carrier of the planetary reducer 4 of this embodiment utilizes a floating connection with the splined transmission shaft 6, while the internal gear ring 10 of the planetary reducer 4 extends toward the hydraulic motor 2, extending outside the splined transmission shaft 6. A low-speed brake 8 (i.e., the housing of the low-speed brake 8 and the internal gear ring 1 are integrally formed) is positioned between the internal gear extension 11 formed and the splined transmission shaft 6, thereby achieving a dual-safety braking function. This effectively addresses the problems of prior art hydraulic transmission brake devices, which suffer from low integration and single functions. In practical applications, multiple components are often required to perform multiple functions, resulting in a complex structure, large size and weight, high cost, and low reliability.

[0059] When in use, this embodiment uses the motor housing (including the spline transmission shaft 6) of the hydraulic motor 2 as the fixed end, and the inner ring gear 10 of the planetary reducer (the housing of the low-speed end brake 8) as the power output end. It can be used for wheel-side drive reducers of various vehicles, thereby simplifying the structure and integrating the drive, brake and clutch into one. In addition, when the clutch is used in this embodiment, it can be used for a mooring winch, and when the clutch is in a normally closed state, it can be used for a safe manned lifting winch. The multifunctional hydraulic transmission brake system of this embodiment integrates the hydraulic motor 2, the clutch (the hydraulic clutch 3), the high-speed end brake 7 and the low-speed end brake 8 into one, and can be hidden in the winch drum. Therefore, it has the characteristics of compact structure, small size, light weight and reliable safety.

[0060] It should be noted that it is obvious to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the present invention. Therefore, from all perspectives, the embodiments should be regarded as illustrative and non-restrictive, and the scope of the present invention is defined by the appended claims rather than the foregoing description. It is intended that all changes that fall within the meaning and range of equivalents of the claims be included in the present invention, and any reference signs in the claims should not be construed as limiting the claims to which they relate.

[0061] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.

Claims

1. A multifunctional hydraulic transmission brake system, characterized in that: include: A hydraulic motor (2), the hydraulic motor (2) comprising an output shaft (5), a rotor (9) and a motor housing, the rotor (9) being sleeved on the output shaft (5), the motor housing extending toward the power output direction of the output shaft (5) to form a hollow spline transmission shaft (6); A hydraulic clutch (3), the hydraulic clutch (3) is located in the spline transmission shaft (6), and one end of the hydraulic clutch (3) is connected to the output shaft (5); the hydraulic clutch (3) is a multi-disc hydraulically controlled normally closed structure, comprising a sleeve (20), a pressure block (21), an I-shaped piston (22) and a top block (23); one end of the sleeve (20) is fixedly connected to the output shaft (5), and the inner wall of the sleeve (20) is provided with a plurality of first fixed friction plates; The pressure block (21) is located in the sleeve (20), the pressure block (21) is fixedly sleeved on the intermediate shaft, a plurality of first dynamic friction plates are provided on the outer periphery of the pressure block (21), and the plurality of first dynamic friction plates and the plurality of first fixed friction plates are arranged alternately; the I-shaped piston (22) is provided at the end of the pressure block (21) away from the output shaft (5), the I-shaped piston (22) is sleeved on the intermediate shaft; the top block (23) is provided between the outer ring recess of the I-shaped piston (22) and the inner wall of the spline transmission shaft (6), a compression spring (24) is provided between the end of the outer ring recess of the I-shaped piston (22) close to the output shaft (5) and the top block (23), and a first oil chamber is provided between the end of the outer ring recess of the I-shaped piston (22) away from the output shaft (5) and the top block (23); A planetary reducer (4), wherein the planetary reducer (4) is connected to the other end of the hydraulic clutch (3) through the intermediate shaft, and the planetary carrier of the planetary reducer (4) is supported on the spline transmission shaft (6) and connected to the spline transmission shaft (6); wherein the intermediate shaft includes a front shaft (14) and a rear shaft (15), the planetary reducer (4) is mounted on the front shaft (14), one end of the rear shaft (15) is connected to the hydraulic clutch (3), and the other end is connected to the end of the front shaft (14) close to the hydraulic clutch (3) through a spline sleeve (16); The inner gear ring (10) of the planetary reducer (4) extends toward an end close to the hydraulic motor (2) to the outside of the spline transmission shaft (6), forming an inner gear ring extension section (11); A hydraulic brake assembly, the hydraulic brake assembly comprising a high-speed end brake (7) and a low-speed end brake (8), the high-speed end brake (7) being arranged between the motor housing and the rotor (9), and the low-speed end brake (8) being arranged between the inner gear ring extension section (11) and the spline transmission shaft (6); A hydraulic valve group (1), wherein the hydraulic valve group (1) is connected to the hydraulic motor (2) and the first oil chamber.

2. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: The rear axle (15) and the spline sleeve (16) are both located inside the spline transmission shaft (6), and a support ring (19) is provided between the outer ring of the spline sleeve (16) and the inner wall of the spline transmission shaft (6); wherein the outer periphery of the support ring (19) is fixed to the inner wall of the spline transmission shaft (6), and a ball bearing is provided between the inner periphery of the support ring (19) and the outer ring of the spline sleeve (16).

3. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: The high-speed end brake (7) is a multi-disc hydraulically controlled normally closed structure, comprising: a second dynamic friction plate, wherein the second dynamic friction plate is disposed on the inner wall of the motor housing, and a plurality of the second dynamic friction plates are disposed along the axial direction of the motor housing; A second fixed friction plate, the second fixed friction plate being arranged on the rotor (9), and a plurality of the second fixed friction plates being arranged along the axial direction of the motor housing, the plurality of the second fixed friction plates and the plurality of the second moving friction plates being arranged alternately; A cylindrical piston (25) is provided, wherein the cylindrical piston (25) is sleeved between the inner wall of the motor housing and the rotor (9); a cover plate (26) is provided at one end of the motor housing away from the hydraulic clutch (3); a compression spring (24) is provided between the end of the cylindrical piston (25) close to the cover plate (26) and the cover plate (26); a second oil chamber is provided between the cylindrical piston (25) and the inner wall of the spline transmission shaft (6); and the second oil chamber is connected to the hydraulic valve group (1).

4. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: The low-speed end brake (8) is a multi-disc hydraulically controlled normally closed structure, comprising: a third dynamic friction plate, the third dynamic friction plate being arranged on the outer periphery of one end of the spline transmission shaft (6) close to the planetary reducer (4), and a plurality of the third dynamic friction plates being arranged along the axial direction of the spline transmission shaft (6); a third fixed friction plate, the third fixed friction plate being arranged on the inner wall of the inner gear ring extension section (11), and a plurality of the third fixed friction plates being arranged along the axial direction of the inner gear ring extension section (11), the plurality of the third fixed friction plates and the plurality of the third dynamic friction plates being arranged alternately; An annular piston (28) is sleeved between the outer wall of the spline transmission shaft (6) and the inner wall of a rear cover (27), and the rear cover (27) is connected to the end of the inner gear ring extension section (11) away from the planetary reducer (4); a compression spring (24) is provided between the annular piston (28) and the inner wall of the rear cover (27), and a third oil chamber is provided between the annular piston (28) and the outer wall of the spline transmission shaft (6), and the third oil chamber is connected to the hydraulic valve group (1).

5. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: The hydraulic motor (2) is a swash plate plunger type hydraulic motor.

6. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: The planetary reducer (4) is a three-stage planetary reducer, which comprises: A first-stage reduction mechanism, the first-stage reduction mechanism comprising a first-stage sun gear (12), a first-stage planetary gear (18) and a first-stage planetary carrier (36), the first-stage sun gear (12) being arranged at an end of the intermediate shaft away from the hydraulic clutch, a plurality of the first-stage planetary gears (18) being meshed with the outer periphery of the first-stage sun gear (12), and the plurality of the first-stage planetary gears (18) being rotatably mounted on the first-stage planetary carrier (36); an end of the inner gear ring (10) away from the hydraulic motor (2) being connected to a front cover (17), and any one of the first-stage planetary gears (18) being meshed with the inner wall of the front cover (17); A secondary reduction mechanism, the secondary reduction mechanism comprising a secondary center wheel (33), secondary planetary wheels (35) and a secondary planetary carrier (34), the secondary center wheel (33) being sleeved on the outer periphery of the intermediate shaft but not connected to the intermediate shaft, the primary planetary carrier (36) being sleeved on the secondary center wheel (33) and key-connected to the secondary center wheel (33); a plurality of secondary planetary wheels (35) being meshed with the outer periphery of the secondary center wheel (33), the plurality of secondary planetary wheels (35) being rotatably mounted on the secondary planetary carrier (34), and any of the secondary planetary wheels (35) being meshed with the inner wall of the inner gear ring extension section (11); The three-stage reduction mechanism comprises a three-stage center wheel (31), three-stage planetary wheels (32) and a three-stage planetary carrier (13). The three-stage center wheel (31) is sleeved on the outer periphery of the intermediate shaft but is not connected to the intermediate shaft. The two-stage planetary carrier (34) is sleeved on the three-stage center wheel (31) and is key-connected to the three-stage center wheel (31). The outer periphery of the three-stage center wheel (31) is meshed with a plurality of the three-stage planetary wheels (32). The plurality of the three-stage planetary wheels (32) are rotatably mounted on the three-stage planetary carrier (13), and any one of the three-stage planetary wheels (32) is meshed with the inner wall of the inner gear ring extension section (11). The three-stage planetary carrier (13) is key-connected to the spline transmission shaft (6).

7. The multifunctional hydraulic transmission brake system according to claim 6, characterized in that: An involute internal spline is formed on the three-stage planetary carrier (13), an involute external spline is provided on the outer wall of the spline transmission shaft (6) at one end away from the hydraulic motor (2), and the three-stage planetary carrier (13) and the end of the spline transmission shaft (6) away from the hydraulic motor (2) are floatingly connected via the involute spline.

8. The multifunctional hydraulic transmission brake system according to claim 1, characterized in that: A spline section (29) for fixing the multifunctional hydraulic transmission brake system is provided at one end of the spline transmission shaft (6) away from the planetary reducer (4); a flange is provided around the outer wall of the inner gear ring extension section (11); and a plurality of fixing holes (30) are provided on the flange at intervals along its circumference.

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