CN214836842U - Wheel-side rotating inner curve low-speed large-torque hydraulic motor - Google Patents

Abstract

The utility model relates to a wheel edge rotates big moment of torsion hydraulic motor of inner curve low-speed comprises fixed cylinder body subassembly, rotary motor casing subassembly, brake disc subassembly and speedtransmitter, and rotary motor casing subassembly is rotatory round fixed cylinder body subassembly. The end face flow distribution mode is adopted, so that the internal leakage is reduced, the abrasion is automatically compensated, the volume efficiency is improved, and the service life is prolonged; the gear meshing brake structure is adopted, and the gear meshing is opened through the spring and the pressure oil, so that the braking and the loosening are realized. Under the condition that the rotating speed and the torque are the same, the motor has the characteristics of compact structure, small overall dimension, light weight, flexible operation, safety, reliability and the like; and a Hall speed sensor is adopted to detect a rectangular pulse signal, so that the motor speed measurement function is realized. The method is widely applied to the industries of walking engineering machinery, ships, hoisting equipment and the like.

Description

Wheel-side rotating inner curve low-speed large-torque hydraulic motor

Technical Field

The utility model relates to a technical field's such as walking engineering machine tool, boats and ships, hoisting equipment low-speed moment of torsion hydraulic motor especially relates to a big moment of torsion hydraulic motor of wheel limit rotation inner curve low-speed.

Background

With the situation that the market of the engineering vehicle is competitive, how to improve the performance of the vehicle, reduce the cost and occupy the market is very important. The wheel driving hydraulic motor used by the prior engineering vehicle has two structural modes, one structure is that an axial plunger hydraulic motor drives a planetary reduction gearbox; one is an inner curve hydraulic motor in which a cylinder (main shaft) rotates and a motor housing is fixed. The first structure has the defects of more parts, complex structure, hydraulic loss, mechanical loss, easy crawling at low speed, high failure rate and the like; in the second structure, the cylinder body (main shaft) rotates, and the motor shell is fixed and does not rotate, so that the inner curve hydraulic motor occupies a large space and is heavy, and the application of the inner curve hydraulic motor in engineering vehicles is limited. Therefore, by improving the structure, on the basis of ensuring the driving performance of the vehicle, the efficiency is improved, the failure rate is reduced, the occupied space is reduced, the layout of the main engine is more reasonable, and the method is a significant subject in the field.

In the industries of ships, hoisting equipment and the like, the traditional inner curve shell rotary motor has different flow distribution forms and brake braking compared with the wheel edge rotating inner curve low-speed large-torque hydraulic motor. A commonly used inner curve shell rotary motor is in a radial flow distribution mode, sealing is achieved through an oil film generated by relative motion between a cylinder body and an oil distribution shaft, the flow distribution mode has strict requirements on machining precision and fit clearance, and meanwhile, the cylinder body and the oil distribution shaft are abraded in the using process, the clearance is increased, the internal discharge capacity is increased, the rated pressure is reduced, and the volumetric efficiency is reduced.

In view of the above-mentioned defects of the existing hydraulic motors, the inventor of the present invention has made extensive studies and designs, and after repeatedly trying out samples and improving the same, finally, has created the utility model with practical value.

Disclosure of Invention

An object of the utility model is to overcome the defect that current hydraulic motor exists, and provide a wheel limit of novel structure and rotate the big moment of torsion hydraulic motor of inner curve low-speed, the technical problem that solve makes it improve the structure, reduces the defect and not enough of wheel drive's walking hydraulic motor structure among the current engineering vehicle, raises the efficiency, reduces the fault rate, reduces occupation space, realizes the required technical performance of engineering vehicle wheel drive to be suitable for the practicality more.

Another object of the utility model is to provide a big moment of torsion hydraulic motor of wheel limit rotation inner curve low-speed, the technical problem that solve makes it have compact structure, overall dimension is little, light in weight, simple to operate, low-speed performance are good, in trades such as walking engineering machine tool, boats and ships, hoisting equipment, have extensive using value to be suitable for the practicality more.

The purpose of the utility model and the technical problem thereof are realized by adopting the following technical scheme. According to the utility model, the wheel-side rotating inner curve low-speed large-torque hydraulic motor comprises a fixed cylinder body assembly, a rotating motor shell assembly, a brake disc assembly and a speed sensor, wherein the motor shell assembly rotates around the fixed cylinder body assembly; wherein the content of the first and second substances,

the fixed cylinder body assembly consists of a cylinder body, a transition ring and a shaft end cover;

the rotary motor shell component is formed by connecting a shell, an inner curve cam ring and a tail end cover by high-strength bolts;

the hydraulic motor brake disc assembly consists of a brake disc and a brake fixing frame, wherein a spline on the inner circumference of the tail end cover is connected with the brake disc, and the bottom of the tail end cover is connected with the brake fixing frame through a screw;

further comprising: the oil distribution disc is arranged on the tail end cover in a floating mode through shifting fork screws; an oil distribution disc spring is arranged between the oil distribution disc and the tail end cover, the oil distribution disc rotates along with the tail end cover through a shifting fork screw, the oil distribution disc spring provides initial attaching force between the oil distribution disc and the end face of the cylinder body, the oil distribution disc moves leftwards along with the pushing of medium pressure generated when high-pressure oil flows into the oil distribution disc through an oil duct, and the oil distribution disc compresses the end face of the cylinder body to realize end face flow distribution.

The purpose of the utility model and the technical problem thereof can be further realized by adopting the following technical measures.

The cylinder body is characterized by further comprising a plunger and a cylindrical roller, wherein a spline on the outer circumference of the left end of the cylinder body is connected with an end cover of the shaft end, the right inner end surface of the cylinder body and the transition ring are connected into a whole by a screw, and the plunger and the cylindrical roller are arranged on the circumference diameter of the cylinder body; a combined bearing and a tapered roller bearing are arranged between the shell and the cylinder body.

Furthermore, the number of plunger holes in the cylinder body and the number of curve actions in the inner curve cam ring are both even numbers, and radial forces acting on the cylinder body are completely balanced; the oil passages comprise a high-pressure oil inlet oil passage and a low-pressure oil return oil passage, a first axial oil passage, a fourth axial oil passage, a first radial right-angle oil passage and a second radial right-angle oil passage are arranged in the cylinder body, a second axial oil passage, a third axial oil passage, a fifth axial oil passage and a sixth axial oil passage are arranged in the transition ring, a first semi-annular oil passage and a second semi-annular oil passage are arranged in the oil distribution disc, the end surfaces of the cylinder body, the transition ring and the oil distribution disc are attached to each other, and the first axial oil passage → the second axial oil passage → the first semi-annular oil passage → the third axial oil passage → the first radial right-angle oil passage high-pressure oil inlet oil passage and the second radial right-angle oil passage → the sixth axial oil passage → the second semi-annular oil passage → the fifth axial oil passage → the low-pressure oil return oil passage; high-pressure oil enters a plunger cavity in a cylinder body through a first axial oil duct → a second axial oil duct → a first semi-annular oil duct → a third axial oil duct → a first radial right-angle oil duct high-pressure oil inlet oil duct, acts on a plunger, a cylindrical roller presses on the curved surface of an inner curve cam ring to generate tangential component force so as to enable a shell assembly to rotate, a cam curve plunger on the other side is pressed into a plunger hole in the cylinder body by the curved surface, and low-pressure oil is discharged through a second radial right-angle oil duct → a sixth axial oil duct → a second semi-annular oil duct → a fifth axial oil duct → a fourth axial oil duct low-pressure oil return oil duct; the high-low oil pressure interface of the hydraulic system is changed, high-pressure oil enters the plunger hole through the fourth axial oil passage → the fifth axial oil passage → the second semi-annular oil passage → the sixth axial oil passage → the second radial right-angle oil passage, and low-pressure oil is discharged through the first radial right-angle oil passage → the third axial oil passage → the first semi-annular oil passage → the second axial oil passage → the first axial oil passage, so that the reverse rotation of the motor is realized.

The oil duct further comprises a brake oil duct, a seventh axial oil duct is arranged in the cylinder body, an eighth axial oil duct is arranged on the transition ring, a first right-angle oil duct is arranged in the oil distribution disc, a third semi-annular oil duct is arranged in the tail end cover, a second right-angle oil duct is arranged in the brake fixing frame, the cylinder body, the transition ring, the oil distribution disc and the sealing sleeve are mutually attached in end surface mode, and the seventh axial oil duct → the eighth axial oil duct → the first right-angle oil duct → the third semi-annular oil duct → the second right-angle oil duct are sequentially formed; the right end face of the cylinder body and the left end face of the brake disc are provided with rectangular teeth; the tail end cover and the brake disc are provided with brake springs; the brake disc is provided with an inner sealing ring and an outer sealing ring, the generated medium pressure overcomes the brake spring force along with the hydraulic oil entering the end face of the brake disc through the brake oil duct, the brake disc is pushed to move to the tail end cover, and the rectangular teeth on the brake disc and the cylinder body are meshed and disengaged; when the brake oil pressure is removed, the brake disc moves leftwards under the action of the brake spring force, and the brake disc is meshed with the rectangular teeth on the cylinder body, so that the brake is realized.

Furthermore, an outer sealing ring and an inner sealing ring are arranged on the oil distribution disc.

A floating seal is arranged between the shell and the end cover of the shaft end; an O-shaped sealing ring is arranged between the shaft end cover and the cylinder body.

Further, the method is simple. The tail end cover is provided with a bolt, and the mechanical brake can be mechanically released under the condition that the hydraulic brake system fails.

Furthermore, a convex-concave groove is formed in the left end face of the shell; the end cover of the shaft end is connected with a speed sensor, and the speed measurement function is realized according to the detected rectangular signal waves.

Compared with the prior art, the utility model obvious advantage and beneficial effect have. By means of the technical scheme, the method at least has the following advantages:

1. the utility model discloses a casing is rotatory, terminal surface distribution form, tooth meshing brake structure, provides an effective way for the application of inner curve hydraulic motor on engineering vehicle. Meanwhile, a new scheme is provided for the wheel driving mode of the engineering vehicle.

2. The utility model adopts a shell rotating structure, compared with a planetary reduction gearbox, the structure is simpler, the efficiency is higher, the stability is higher in low speed, the weight is light, the volume is small, the manufacture and the processing are easier, and the failure rate is low; compared with a cylinder body rotating hydraulic motor, the hydraulic motor occupies smaller space and is beneficial to the layout of a host machine.

3. The utility model discloses compare with the rotatory hydraulic motor of traditional casing, the distribution form is different. Traditional casing rotary motor is radial distribution form, and the oil film that relative motion produced between cylinder body and the oil distribution shaft realizes sealed, and is very strict to precision and fit clearance requirement, and cylinder body and oil distribution shaft have wearing and tearing in the use simultaneously, and the clearance increases, and the internal discharge of motor increases, and the volumetric efficiency reduces, and engineering machine tool can't normally work. The utility model discloses a terminal surface join in marriage a class form, the volume of having reduced internal discharge and automatic compensation wearing and tearing reduce the processing degree of difficulty, improve the volume efficiency, increase of service life. The method has wide application value in the industries of walking engineering machinery, ships, hoisting equipment and the like.

4. The utility model discloses compare with the rotatory hydraulic motor of traditional casing, the brake braking structure is different. The traditional motor brake basically adopts a belt type brake structure on a shell, and a brake bracket is required to be arranged independently, so that the axial size of the motor brake is increased. The wheel edge rotation inner curve low-speed large-torque hydraulic motor adopts a tooth meshing brake structure, and the opening of tooth meshing is realized through spring force and pressure oil, so that the braking and the loosening are realized. Under the condition of the same rotating speed and torque, the wheel-side rotating inner curve low-speed large-torque hydraulic motor has the characteristics of compact structure, small overall dimension, light weight, flexible operation, safety, reliability and the like.

5. The utility model discloses a hall speedtransmitter detects rectangular pulse signal, realizes the motor function of testing the speed.

The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical means of the present invention more clearly understood, the present invention may be implemented according to the content of the description, and in order to make the above and other objects, features, and advantages of the present invention more obvious and understandable, the following preferred embodiments are described in detail with reference to the accompanying drawings.

Drawings

FIG. 1 is a schematic view of the structure of the low-speed large-torque hydraulic motor with the inner curve rotated by the wheel of the present invention

FIG. 2 is the structural schematic diagram II of the low-speed large-torque hydraulic motor with the wheel-side rotating inner curve

FIG. 3 is a schematic view of the structure of the low-speed large-torque hydraulic motor with a wheel-side rotating inner curve of the present invention

FIG. 4A is the schematic diagram of the wheel-side rotating inner curve low-speed large-torque hydraulic motor end surface flow distribution from the A port oil inlet

FIG. 4B is the schematic diagram of the end face flow distribution of the wheel-side rotating inner curve low-speed large-torque hydraulic motor with oil return from the port A

FIG. 5 is a schematic view of the braking oil path of the low-speed large-torque hydraulic motor with inner curve for wheel rim rotation of the present invention

Description of reference numerals:

1: the speed sensor 2: end cover of shaft end

3: the shell 4: cylinder body

5: inner curve cam ring 6: transition ring

7: end cap 8: brake disc

9: brake mount 10: brake screw

11: oil distribution pan 12: outer sealing ring

13: inner seal ring 14: oil distribution disc spring

15: sealing sleeve 16: spring

17: inner seal ring 18: outer sealing ring

19: bolt 20: plunger piston

21: cylindrical roller 22: shifting fork screw

23: screw 24: brake spring

25: the combination bearing 26: tapered roller bearing

27: floating seal 28: o-shaped sealing ring

A1: first axial oil passage a 2: second axial oil duct

A3: the first semi-annular oil passage a 4: third axial oil passage

A5: first radial right-angle oil passage

C1: the fourth axial oil passage C2: fifth axial oil duct

C3: the second semi-annular oil passage C4: sixth axial oil passage

C5 second radial right-angle oil passage

X1: the seventh axial oil passage X2: eighth axial oil passage

X3: the first straight angle oil passage X4: third semi-annular oil duct

X5 second right-angle oil passage

Detailed Description

To further illustrate the technical means and effects of the present invention for achieving the objects of the present invention, the following detailed description of the embodiments, structures, features and effects of the low-speed high-torque hydraulic motor with wheel-side rotation inner curve according to the present invention will be made with reference to the accompanying drawings and preferred embodiments.

As shown in fig. 1 to 3, the wheel-side rotating inner curve low-speed large-torque hydraulic motor according to the preferred embodiment of the present invention is integrally composed of four parts, namely, a fixed cylinder body assembly, a rotating motor housing assembly, a brake disc assembly and a speed sensor, wherein the motor housing assembly rotates around the fixed cylinder body assembly. The device mainly comprises a speed sensor 1, a shaft end cover 2, a shell 3, a cylinder body 4, an inner curve cam ring 5, a transition ring 6, a tail end cover 7, a brake disc 8, a brake fixing frame 9 and an oil distribution disc 11. The cylinder body 4, the transition ring 6 and the shaft end cover 2 form a fixed cylinder body assembly; the shell 3, the inner curve cam ring 5 and the tail end cover 7 are connected through high-strength bolts 19 to form a motor shell rotating assembly, and the brake disc 8 and the brake fixing frame 9 form a hydraulic motor brake disc assembly.

The spline on the outer circumference of the left end of the cylinder body 4 is connected with the shaft end cover 2.

The right inner end surface of the cylinder body 4 and the transition ring 6 are connected into a whole by screws, and a plunger 20 and a cylindrical roller 21 are arranged on the circumference diameter of the cylinder body 4.

The spline on the inner circumference of the tail end cover 7 is connected with a brake disc 8, and the bottom of the tail end cover 7 is fixed with a brake fixing frame 9 through a screw 23.

A combination bearing 25 and a tapered roller bearing 26 are provided between the housing 3 and the cylinder block 4.

As shown in fig. 4A and 4B, the number of plunger holes in the cylinder 4 and the number of curve operations in the inner curve cam ring 5 are both even, and the radial forces acting on the cylinder 4 are completely balanced. The cylinder block 4 is internally provided with a first axial oil passage A1, a fourth axial oil passage C1, a first radial right-angle oil passage A5 and a second radial right-angle oil passage C5, the transition ring 6 is internally provided with a second axial oil passage A2, a third axial oil passage A4, a fifth axial oil passage C2 and a sixth axial oil passage C4, and the oil distribution disc 11 is internally provided with a first semi-annular oil passage A3 and a second semi-annular oil passage C3. The cylinder block 4, the transition ring 6, and the oil distribution disc 11 are fitted to each other in end face, and a first axial oil passage a1 → a second axial oil passage a2 → a first semi-annular oil passage A3 → a third axial oil passage a4 → a first radial right-angle oil passage a5 high-pressure oil inlet oil passage and a second radial right-angle oil passage C5 → a sixth axial oil passage C4 → a second semi-annular oil passage C3 → a fifth axial oil passage C2 → a fourth axial oil passage C1 low-pressure oil return passage are sequentially formed.

As shown in fig. 2, the oil distribution pan 11 is float-mounted on the end cap 7 by means of a fork screw 22.

An oil distribution disc spring 14 is arranged between the oil distribution disc 11 and the tail end cover 8; an outer sealing ring 12 and an inner sealing ring 13 are arranged on the oil distribution disc 11. The oil distribution disc 11 rotates along with the tail end cover 7 through the shifting fork screw 22, an oil distribution disc spring provides initial pressing force between the oil distribution disc and the end face of the cylinder body, medium pressure is generated to push the oil distribution disc to move leftwards along with the fact that high-pressure oil flows into the oil distribution disc, the oil distribution disc is tightly pressed on the end face of the cylinder body to achieve pressure self sealing, internal leakage is reduced, and abrasion is automatically compensated.

As shown in fig. 5, a seventh axial oil passage X1 is arranged in the cylinder block 4, the transition ring 6 is provided with an eighth axial oil passage X2, the oil distribution disc 11 is provided with a first right-angle oil passage X3, the tail end cover 7 is provided with a third semi-annular oil passage X4, the brake disc fixing frame 9 is provided with a second right-angle oil passage X5, the cylinder block 4, the transition ring 6, the oil distribution disc 11 and the sealing sleeve 15 are attached to each other in end face, and the seventh axial oil passage X1 → the eighth axial oil passage X2 → the first right-angle oil passage X3 → the third semi-annular oil passage X4 → the second right-angle oil passage X5 are sequentially formed.

As shown in figures 1 and 2, the right end surface of the cylinder body 4 and the left end surface of the brake disc 8 are provided with rectangular teeth. A seal sleeve 15 and a spring 16 are arranged between the oil distribution disc 11 of the tail end cover 7. A brake spring 24 is arranged between the tail end cover 8 and the brake disc 13. The brake disc 8 is provided with an inner sealing ring 17 and an outer sealing ring 18, the brake oil enters the end face of the brake disc to generate medium pressure, the elasticity of a brake spring is overcome, the brake disc 8 is pushed to move to the tail end cover 7, the engaging teeth on the brake disc 8 and the cylinder body 4 are disengaged, and the motor can work. When the brake oil pressure is removed, the brake disc 8 moves leftwards under the action of the brake spring force, and the brake disc 8 is meshed with the rectangular teeth on the cylinder body 4, so that the brake is realized.

The end cap 7 is provided with a bolt 10 to mechanically disengage the brake in the event of a failure of the hydraulic brake system.

As shown in fig. 1, the left end surface of the shell 3 is provided with a convex-concave groove; and the shaft end cover 2 is provided with a speed sensor 1, and the speed measurement function is realized by measuring a generated rectangular wave signal.

As shown in fig. 1 and 5, the brake disc 8 is provided with an inner seal 17 and an outer seal 18; and a sealing sleeve 15 and a spring 16 are arranged at a brake oil port of the oil distribution disc 11 to prevent a hydraulic oil path from leaking.

As shown in fig. 1, a floating seal 27 is arranged between the housing 3 and the shaft end cover 2, and an O-ring 28 is arranged between the shaft end cover 2 and the cylinder 4 to prevent hydraulic oil in the housing from leaking.

The utility model discloses the wheel limit rotates the big moment of torsion hydraulic motor of inner curve low-speed and is adapted to trades such as walking engineering machine tool, boats and ships, hoisting equipment.

The utility model discloses the wheel limit rotates inner curve low-speed big moment of torsion hydraulic motor's action process as follows:

before the hydraulic motor works, hydraulic oil enters the end face of the brake disc 8 through the seventh axial oil channel X1 → the eighth axial oil channel X2 → the first right-angle oil channel X3 → the third semi-annular oil channel X4 → the second right-angle oil channel X5, medium pressure is generated due to the area difference between the inner seal 17 and the outer seal 18, the brake disc 8 overcomes the elastic force of the brake spring 24, the brake disc moves to the end face of the tail end cover 8, rectangular teeth on the brake disc 13 and the cylinder body 3 are disengaged, and the motor can work.

When the hydraulic motor works normally, high-pressure oil enters the plunger cavity in the cylinder body 4 through the first axial oil passage A1 → the second axial oil passage A2 → the first semi-annular oil passage A3 → the third axial oil passage A4 → the first radial right-angle oil passage A5, acts on the plunger 20, the cylindrical roller 21 presses on the curved surface of the inner curve cam ring 5 to generate tangential component force, so that the shell assembly rotates, the cam curve plunger 20 on the other side is pressed into a plunger hole in the cylinder body 4 by the curved surface, and low-pressure oil is discharged through the second radial right-angle oil passage C5 → the sixth axial oil passage C4 → the second semi-annular oil passage C3 → the fifth axial oil passage C2 → the fourth axial oil passage C1 to form a low-pressure return oil passage. The high and low oil pressure interfaces of the hydraulic system are changed, high-pressure oil enters the plunger hole through the fourth axial oil passage C1 → the fifth axial oil C2 → the second semi-annular oil passage C3 → the sixth axial oil passage C4 → the second radial right-angle oil passage C5, and low-pressure oil is discharged through the oil passages, namely, the first radial right-angle oil passage a5 → the third axial oil passage a4 → the first semi-annular oil passage A3 → the second axial oil passage a2 → the first axial oil passage a1, so that the reverse rotation of the motor is realized. When the oil distribution disc 11 distributes oil, hydraulic oil flows into the rear end face of the first semi-annular oil passage a1 → the second axial oil passage a2 → the first semi-annular oil passage A3 or the fourth axial oil passage C1 → the fifth axial oil passage C2 → the second semi-annular oil passage C3, the oil distribution disc spring 14 provides initial pressing force, and as the hydraulic oil flows into the oil distribution disc 11, medium pressure is generated to push the oil distribution disc 11 to move axially to the left to press the end face of the cylinder 4 to realize pressure self-sealing. By adopting an end face flow distribution mode, the oil distribution disc 11 completes the flow distribution action of high requirement oil inlet and low pressure oil return of the plunger hole on the cylinder body 4, and the continuous rotation of the motor shell is realized.

When braking is needed, oil pressure is removed, the brake disc 8 moves leftwards under the action of the brake spring 24, and the brake disc 8 is meshed with the rectangular teeth on the cylinder body 4, so that braking is realized. When the hydraulic brake system fails, the brake screw 10 can be screwed down to loosen the brake.

The left shaft end of the shell 3 is provided with a convex-concave groove. When the shell 3 rotates relatively, the speed sensor 1 generates a rectangular pulse signal, and the motor speed measurement function is realized.

The above description is only a preferred embodiment of the present invention, and the present invention is not limited to the above embodiments, and although the present invention has been disclosed with the preferred embodiments, it is not limited to the present invention, and any skilled person in the art can make some modifications or equivalent embodiments without departing from the scope of the present invention, but all the technical matters of the present invention are within the scope of the present invention.

Claims (7)

1. The utility model provides a big moment of torsion hydraulic motor of wheel limit rotation inner curve low-speed which characterized in that: the brake disc comprises a fixed cylinder body assembly, a rotary motor shell assembly, a brake disc assembly and a speed sensor, wherein the motor shell assembly rotates around the fixed cylinder body assembly; wherein the content of the first and second substances,

the fixed cylinder body component consists of a cylinder body (4), a transition ring (6) and a shaft end cover (2);

the rotary motor shell component is formed by connecting a shell (3), an inner curve cam ring (5) and a tail end cover (7) by using a high-strength bolt (19);

the hydraulic motor brake disc assembly consists of a brake disc (8) and a brake fixing frame (9), wherein a spline on the inner circumference of the tail end cover (7) is connected with the brake disc (8), and the bottom of the tail end cover (7) is connected with the brake fixing frame (9) through a screw (23);

further comprising: the oil distribution ring is characterized by comprising an inner curve cam ring (5), a transition ring (6) and an oil distribution disc (11), wherein the oil distribution disc (11) is arranged on a tail end cover (7) in a floating mode through a shifting fork screw (22); an oil distribution disc spring (14) is arranged between the oil distribution disc (11) and the tail end cover (7), the oil distribution disc (11) rotates along with the tail end cover (7) through a shifting fork screw (22), the oil distribution disc spring (14) provides initial attaching force between the oil distribution disc and the end face of the cylinder body, medium pressure is generated when high-pressure oil flows into the oil distribution disc (11) through an oil duct to push the oil distribution disc (11) to move leftwards, and the oil distribution disc (11) is tightly pressed on the end face of the cylinder body (4) to realize end face flow distribution.

2. The hub rotation inside curve low speed high torque hydraulic motor of claim 1, wherein: the cylinder is characterized by further comprising a plunger (20) and a cylindrical roller (21), wherein a spline on the outer circumference of the left end of the cylinder body (4) is connected with the shaft end cover (2), the right inner end surface of the cylinder body (4) and the transition ring (6) are connected into a whole through a screw, and the plunger (20) and the cylindrical roller (21) are arranged on the circumference diameter of the cylinder body (4); a combined bearing (25) and a tapered roller bearing (26) are arranged between the shell (3) and the cylinder body (4).

3. The hub rotation inside curve low-speed high-torque hydraulic motor according to any one of claims 1-2, wherein: the number of plunger holes in the cylinder body (4) and the number of curve actions in the inner curve cam ring (5) are both even numbers, and radial forces acting on the cylinder body (4) are completely balanced; the oil passages comprise a high-pressure oil inlet passage and a low-pressure oil return passage, a first axial oil passage (A1), a fourth axial oil passage (C1), a first radial right-angle oil passage (A5) and a second radial right-angle oil passage (C5) are arranged in the cylinder body (4), a second axial oil passage (A2), a third axial oil passage (A4), a fifth axial oil passage (C2) and a sixth axial oil passage (C4) are arranged in the transition ring (6), a first semi-annular oil passage (A3) and a second semi-annular oil passage (C3) are arranged in the oil distribution plate (11), the cylinder body (4), the transition ring (6) and the oil distribution plate (11) are mutually attached in end face mode, and a first axial oil passage (A1) → second axial oil passage (A2) → first semi-annular oil passage (A3) → third axial oil passage (A4) → first radial right-angle oil passage (A5) and a second radial right-angle oil passage (C638) → second axial fifth axial oil passage (C4) → fifth axial oil passage (C638) → fifth axial oil passage (C4) are sequentially formed A four-axial oil passage (C1) low pressure return oil passage; high-pressure oil enters an inner plunger cavity of the cylinder body (4) through a first axial oil passage (A1) → a second axial oil passage (A2) → a first semi-annular oil passage (A3) → a third axial oil passage (A4) → a first radial right-angle oil passage (A5), acts on the plunger (20), a cylindrical roller (21) presses on a curved surface of an inner curve cam ring (5) to generate a tangential component force, so that the shell assembly rotates, the other side cam curve plunger (20) is pressed into a plunger hole in the cylinder body (4) by the curved surface, and low-pressure oil is discharged through a second radial right-angle oil passage (C5) → a sixth axial oil passage (C4) → a second semi-annular oil passage (C3) → a fifth axial oil passage (C2) → a fourth axial oil passage (C1) low-pressure oil return passage; changing a high-low oil pressure interface of a hydraulic system, high-pressure oil enters a plunger hole through a fourth axial oil passage (C1) → a fifth axial oil passage (C2) → a second semi-annular oil passage (C3) → a sixth axial oil passage (C4) → a second radial right-angle oil passage (C5), and low-pressure oil is discharged through an oil passage first radial right-angle oil passage (A5) → a third axial oil passage (A4) → a first semi-annular oil passage (A3) → a second axial oil passage (A2) → a first axial oil passage (A1), so that reverse rotation of a motor is achieved.

4. The hub rotation inside curve low-speed high-torque hydraulic motor according to any one of claims 1-2, wherein: the oil passages further comprise brake oil passages, a seventh axial oil passage (X1) is arranged in the cylinder body (4), an eighth axial oil passage (X2) is arranged in the transition ring (6), a first straight-angle oil passage (X3) is arranged in the oil distribution disc (11), a third semi-annular oil passage (X4) is arranged in the tail end cover (7), a second straight-angle oil passage (X5) is arranged in the brake fixing frame (9), the cylinder body (4), the transition ring (6), the oil distribution disc (11) and the sealing sleeve (15) are mutually attached in end face mode, and a seventh axial oil passage (X1) → an eighth axial oil passage (X2) → a first straight-angle oil passage (X3) → a third semi-annular oil passage (X4) → a second straight-angle oil passage (X5) brake oil passage are sequentially formed; rectangular teeth are arranged on the right end face of the cylinder body (4) and the left end face of the brake disc (8); the tail end cover (7) and the brake disc (8) are provided with brake springs (24); an inner sealing ring (17) and an outer sealing ring (18) are arranged on the brake disc (8), the generated medium pressure overcomes the brake spring force along with the hydraulic oil entering the end face of the brake disc through the brake oil duct, the brake disc (8) is pushed to move to the tail end cover (7), and the rectangular teeth on the brake disc (8) and the cylinder body (4) are meshed and disengaged; when the brake oil pressure is removed, the brake disc (8) moves leftwards under the action of the brake spring force, and the brake disc (8) is meshed with the rectangular teeth on the cylinder body (4) to realize brake.

5. The hub rotation inside curve low speed high torque hydraulic motor of claim 1, wherein: an outer sealing ring (12) and an inner sealing ring (13) are arranged on the oil distribution disc (11);

a floating seal (27) is arranged between the shell (3) and the shaft end cover (2); an O-shaped sealing ring (28) is arranged between the shaft end cover (2) and the cylinder body (4).

6. The hub rotation inside curve low speed high torque hydraulic motor of claim 1, wherein: and a bolt (10) is arranged on the tail end cover (7), and the mechanical brake can be mechanically released under the condition that the hydraulic brake system fails.

7. The hub rotation inside curve low speed high torque hydraulic motor of claim 1, wherein: the left end face of the shell (3) is provided with a convex-concave groove; and the shaft end cover (2) is connected with the speed sensor (1) and realizes a speed measuring function according to the detected rectangular signal waves.

Images