CN112302861A

CN112302861A - Disc flow distribution hydraulic motor

Info

Publication number: CN112302861A
Application number: CN202011068094.8A
Authority: CN
Inventors: 葛玉珍; 岳彩举; 张学忠
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-10-08
Filing date: 2020-10-08
Publication date: 2021-02-02

Abstract

The invention discloses a disc flow distribution hydraulic motor, which comprises a stator and a rotor, wherein the stator is fixedly provided with a middle disc at the left end of a rotating hole, and a connecting disc is fixedly arranged at the right end of the rotating hole; a right end cover is fixedly arranged at the right end of the connecting disc, an output shaft is rotatably connected in the right end cover, a valve block is fixedly arranged at the left end of the middle disc, and a valve plate is rotatably connected in the valve block; the left end of the valve block is provided with a P port and a T port; the inner side wall of the rotating hole is provided with a plurality of needle teeth, and the rotor is eccentrically arranged in the rotating hole; a meshing cavity is formed between the rotor and the plurality of needle teeth in the rotary hole; a variable control assembly is arranged in the valve block, and when the oil pressure of the port P is greater than the set pressure of the variable control assembly, the variable oil groove is communicated with the port T; when the oil pressure of the port P is smaller than the set pressure of the variable control assembly, the variable oil groove is communicated with the port P; the disc flow distribution hydraulic motor is simple in structure and can automatically adjust the discharge capacity according to the pressure of the P port.

Description

Disc flow distribution hydraulic motor

Technical Field

The invention belongs to the technical field of hydraulic motors, and particularly relates to a disc flow distribution hydraulic motor.

Background

The cycloid hydraulic motor is a low-speed large-torque motor, and has the advantages of small volume, high unit power density, high efficiency, wide rotating speed range and the like, so that the cycloid hydraulic motor is widely applied. The basic structure of the cycloid hydraulic motor is that a body shell or a rear cover is provided with a liquid inlet and a backflow port, one end of the cycloid pin gear meshing pair and a flow distribution mechanism are arranged, the flow distribution mechanism can be placed in front of or behind the cycloid pin gear meshing pair, the general plane flow distribution is arranged at the rear, and the other end of the cycloid pin gear meshing pair is provided with an output shaft. And a rotor of the cycloidal pin gear meshing pair is meshed with an external gear at one end of the linkage shaft through an internal spline, and the other end of the linkage shaft is in transmission connection with the output shaft. When the cycloidal pin gear pair works, the flow distribution mechanism enables the liquid inlet to be communicated with the expansion meshing cavity of the cycloidal pin gear pair and enables the contraction cavity of the cycloidal pin gear pair to be communicated with the reflux port. After entering the rear cover from the liquid inlet, pressure liquid enters an expansion meshing cavity formed by the cycloid pin gear meshing pair, so that the volume of the expansion meshing cavity is continuously enlarged, and meanwhile, liquid in a contraction meshing cavity formed by the cycloid pin gear meshing pair flows back from the return port; in the process, the rotor of the cycloidal pin gear meshing pair is driven to rotate by the pressure difference between the expansion meshing cavity and the contraction meshing cavity, and the rotation is transmitted to the output shaft through the linkage shaft to be output, so that the conversion from hydraulic energy to mechanical energy is realized. Meanwhile, the flow distribution mechanism is also driven by the linkage shaft to rotate, and the communication state is switched repeatedly and continuously, so that the conversion process is continued, and the motor can continuously output torque.

The displacement of the disc-port cycloid hydraulic motor in the prior art is fixed, and if the displacement needs to be changed, the structure of the motor needs to be changed integrally, such as the structure of a port plate and a rotor, so that the structure is complex, the cost is high, and the displacement value is not changed conveniently according to the actual situation.

Disclosure of Invention

The invention aims to provide a disc-type hydraulic motor which is simple in structure and can automatically adjust the displacement according to the pressure of a P port.

In order to solve the technical problem, the invention provides a disc flow distribution hydraulic motor which comprises a stator and a rotor, wherein a rotary hole penetrating left and right is formed in the stator, a middle disc is fixedly arranged at the left end of the rotary hole of the stator, and a connecting disc is fixedly arranged at the right end of the rotary hole of the stator; the right end of the connecting disc is fixedly provided with a right end cover, an output shaft is rotatably connected in the right end cover, the left end of the middle disc is fixedly provided with a valve block, a rotary groove is formed in the end face, facing the middle disc, of the valve block, and a valve plate is rotatably connected in the rotary groove; the left end of the valve block is provided with a P port and a T port; the inner side wall of the rotating hole is uniformly provided with a plurality of needle teeth at intervals along the circumferential direction, the rotor is eccentrically arranged in the rotating hole and is in contact with the plurality of needle teeth, and the rotor is synchronously and rotatably connected with the valve plate and the output shaft; a plurality of meshing cavities between the middle disc and the connecting disc are formed in the rotary hole between the rotor and the plurality of needle teeth;

a plurality of through-flow holes which are in one-to-one correspondence with the meshing cavities and are communicated with the meshing cavities are uniformly arranged in the middle disc at intervals along the circumferential direction, a plurality of variable oil grooves and a plurality of oil inlet grooves communicated with the P port are arranged in the valve plate at intervals along the circumferential direction, and the oil inlet grooves and the variable oil grooves are identical in number and are arranged in the valve plate at intervals; oil return grooves communicated with the T port are formed between adjacent variable oil grooves and adjacent oil inlet grooves in the valve plate; the oil inlet groove, the oil return groove and the variable oil groove are communicated with the through flow holes, and are sequentially communicated with the through flow holes along with the rotation of the valve plate according to the sequence of the oil inlet groove, the oil return groove, the variable oil groove and the oil return groove; a variable control assembly is arranged in the valve block, and when the oil pressure of the port P is greater than the set pressure of the variable control assembly, the variable oil groove is communicated with the port T; when the oil pressure of the port P is smaller than the set pressure of the variable control assembly, the variable oil groove is communicated with the port P.

Furthermore, the variable control assembly comprises an annular variable turntable, the left end of the valve plate is provided with a left annular groove, and the variable turntable is rotatably connected in the left annular groove; an arc-shaped groove is formed in the right end of the left annular groove in the valve plate, a baffle plate extending into the arc-shaped groove is arranged at the right end of the variable rotary plate, a control cavity communicated with the P port is formed between the baffle plate and one end of the arc-shaped groove in the arc-shaped groove, a cavity communicated with the T port is formed between the baffle plate and the other end of the arc-shaped groove, and a variable torsion spring for forcing the variable rotary plate to drive the baffle plate to move towards the direction of the compression control cavity is arranged at the left end of the rotary groove in the valve block; the set pressure of the variable control component is the pressure set by the variable torsion spring; the right end of the variable rotary table is provided with a first annular groove communicated with the variable oil groove, when the oil pressure of the port P is greater than the set pressure of the variable torsion spring, the variable rotary table is rotated to a high-pressure working position, and the first annular groove is communicated with the port T; when the oil pressure of the port P is smaller than the set pressure of the variable torsion spring, the variable turntable rotates to the initial working position, and the first annular groove is communicated with the port P.

Further, an oil inlet hole communicated with the port P is axially formed in the valve plate; a first oil return hole and a first oil inlet hole which are communicated with the first ring groove are formed in the variable rotary table; a second oil return hole communicated with the oil return groove and a second oil inlet hole communicated with the oil inlet hole are formed in the valve plate; when the variable turntable is rotated to a high-pressure working position, the first oil return hole is communicated with the second oil return hole, and the first oil inlet hole is disconnected with the second oil inlet hole; when the variable turntable rotates to the initial working position, the first oil return hole is disconnected with the second oil return hole, and the first oil inlet hole is communicated with the second oil inlet hole.

Furthermore, a third oil inlet hole used for communicating the oil inlet groove and the oil inlet hole and a variable oil hole used for communicating the variable oil groove and the first ring groove are formed in the valve plate.

Furthermore, a third oil return hole used for communicating the cavity and one of the oil return grooves and a fourth oil inlet hole used for communicating the control cavity and the oil inlet hole are formed in the valve plate.

Furthermore, an oil return ring groove used for communicating the oil return grooves and the T port is formed in the left end of the valve plate.

Furthermore, the rotor and the valve plate are in synchronous rotating connection through a left linkage shaft, and the rotor and the output shaft are in synchronous rotating connection through a right linkage shaft.

Furthermore, the number of the meshing cavities and the number of the through flow holes are nine; the number of the oil inlet grooves and the number of the variable oil grooves are four; the number of the oil return grooves is eight.

Advantageous effects

Compared with the prior art, the technical scheme of the invention has the following advantages:

the invention can change the number of the meshing cavities communicated with the P port by arranging the variable rotary table and changing the rotating angle of the variable rotary table through hydraulic control pressure, thereby changing the displacement of the hydraulic motor.

Drawings

FIG. 1 is a cross-sectional view of the present invention;

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

FIG. 3 is a cross-sectional view taken along line B-B of FIG. 1;

FIG. 4 is a cross-sectional view of the port plate in the direction C-C of FIG. 1;

FIG. 5 is a cross-sectional view taken in the direction D-D of FIG. 4;

FIG. 6 is a cross-sectional view taken in the direction E-E of FIG. 5;

FIG. 7 is a cross-sectional view at a first displacement in the direction F-F of FIG. 5;

FIG. 8 is a cross-sectional view at a second displacement, taken along the line F-F in FIG. 5.

Detailed Description

Referring to fig. 1 to 8, the present invention provides a disc-type fluid distribution hydraulic motor, including a stator 102 and a rotor 2, wherein the stator 102 is provided with a left-right through rotating hole 102a, the stator 102 is fixedly provided with a middle disc 103 at the left end of the rotating hole 102a, and a connecting disc 104 is fixedly provided at the right end; a right end cover 105 is fixedly installed at the right end of the connecting disc 104, an output shaft 9 is rotatably connected in the right end cover 105, a valve block 101 is fixedly installed at the left end of the middle disc 103, a rotary groove 101a is formed in the end face, facing the middle disc 103, of the valve block 101, and a valve plate 5 is rotatably connected in the rotary groove 101 a; the left end of the valve block 101 is provided with a P port and a T port; the inner side wall of the rotating hole 102a is uniformly provided with a plurality of needle teeth 3 at intervals along the circumferential direction, the rotor 2 is eccentrically arranged in the rotating hole 102a and is in contact with the plurality of needle teeth 3, the rotor 2 is synchronously and rotatably connected with the port plate 5 and the output shaft 9, the rotor 2 and the port plate 5 are synchronously and rotatably connected through a left linkage shaft 4, and the rotor 2 and the output shaft 9 are synchronously and rotatably connected through a right linkage shaft 8; the rotary hole 102a is formed with a plurality of meshing cavities 2a between the intermediate disk 103 and the connecting disk 104 between the rotor 2 and the plurality of pins 3.

A plurality of through-flow holes 1031 which are in one-to-one correspondence with the meshing cavities 2a and are communicated with the meshing cavities are uniformly arranged in the middle disc 103 at intervals along the circumferential direction, a plurality of variable oil grooves 55 and a plurality of oil inlet grooves 54 communicated with the port P are arranged in the valve plate 5 at intervals along the circumferential direction, and the oil inlet grooves 54 and the variable oil grooves 55 are arranged in the valve plate 5 at the same number and at equal intervals; oil return grooves 53 communicated with the T port are formed between adjacent variable oil grooves 55 and adjacent oil inlet grooves 54 in the valve plate 5; the oil inlet groove 54, the oil return groove 53 and the variable oil groove 55 are communicated with the plurality of through holes 1031, and are sequentially communicated with the plurality of through holes 1031 along with the rotation of the valve plate 5 according to the sequence of the oil inlet groove 54, the oil return groove 53, the variable oil groove 55 and the oil return groove 53; a variable control assembly is arranged in the valve block 101, and when the oil pressure of the port P is greater than the set pressure of the variable control assembly, the variable oil groove 55 is communicated with the port T; when the oil pressure at the port P is lower than the set pressure of the variable control unit, the variable oil groove 55 communicates with the port P.

In this embodiment, the variable control assembly includes an annular variable dial 6, a left annular groove 501 is formed at the left end of the thrust plate 5, and the variable dial 6 is rotatably connected in the left annular groove 501; an arc-shaped groove 502 is formed in the right end of a left annular groove 501 in the valve plate 5, a baffle 601 extending into the arc-shaped groove 502 is arranged at the right end of the variable rotating disc 6, a control cavity 58 communicated with a P port is formed in the arc-shaped groove 502 at one end of the baffle 601 and the arc-shaped groove 502, a cavity 59 communicated with a T port is formed between the baffle 601 and the other end of the arc-shaped groove 502, and a variable torsion spring 7 for forcing the variable rotating disc 6 to drive the baffle 601 to move towards the direction of compressing the control cavity 58 is arranged at the left end of a rotating groove 101a in the valve block 101; the set pressure of the variable control component is the pressure set by the variable torsion spring 7; a first annular groove 62 communicated with the variable oil groove 55 is formed in the right end of the variable rotary disc 6, when the oil pressure of the port P is larger than the set pressure of the variable torsion spring 7, the variable rotary disc 6 rotates to a high-pressure working position, and the first annular groove 62 is communicated with the port T; when the oil pressure of the port P is smaller than the set pressure of the variable torsion spring 7, the variable rotary disc 6 rotates to the initial working position, and the first annular groove 62 is communicated with the port P. An oil inlet 52 communicated with the port P is axially arranged in the valve plate 5; a first oil return hole 64 and a first oil inlet hole 63 which are communicated with the first ring groove 62 are formed in the variable rotary table 6; a second oil return hole 511 communicated with the oil return groove 53 and a second oil inlet hole 512 communicated with the oil inlet hole 52 are formed in the valve plate 5; when the variable turntable 6 rotates to a high-pressure working position, the first oil return hole 64 is communicated with the second oil return hole 511, and the first oil inlet hole 63 is disconnected with the second oil inlet hole 512; when the variable capacity rotary table 6 rotates to the initial working position, the first oil return hole 64 is disconnected from the second oil return hole 511, and the first oil inlet hole 63 is communicated with the second oil inlet hole 512.

In this embodiment, the port plate 5 is provided with a third oil inlet hole 52a for communicating the oil inlet groove 54 and the oil inlet hole 52, and a variable oil hole 56 for communicating the variable oil groove 55 and the first ring groove 62. A third oil return hole 510 for communicating the cavity 59 with one of the oil return grooves 53 and a fourth oil inlet hole 57 for communicating the control chamber 58 with the oil inlet hole 52 are formed in the port plate 5. And an oil return ring groove 51 for communicating a plurality of oil return grooves 53 and a T port is formed at the left end of the valve plate 5.

In this embodiment, the number of the engagement cavities 2a and the number of the through-flow holes 1031 are nine; the number of the oil inlet grooves 54 and the number of the variable oil grooves 55 are four; the number of the oil return grooves 53 is eight.

The invention is provided with a port P and a port T, wherein the port P is communicated with high-pressure oil, and the port T is communicated with an oil tank. The port P is also connected to the control chamber 58, and can control the working position of the variable rotary table 6 by the load pressure, the variable rotary table 6 has two working positions, an initial working position and a high pressure working position, when the oil pressure of the port P is smaller than the set pressure of the variable torsion spring 7, the variable rotary table 6 works at the initial working position (as shown in fig. 7) under the acting force of the variable torsion spring 7, and when the oil pressure of the port P is larger than the set pressure of the variable torsion spring 7, the variable rotary table 6 is reversed to the high pressure working position (as shown in fig. 8). As shown in fig. 3, nine meshing cavities 2a are formed among the rotor 2, the needle teeth 3, and the stator 102, and the nine meshing cavities 2a are respectively communicated with the distribution holes, which are located in the circumferential direction of the intermediate disk 103.

As shown in fig. 1-4, hydraulic oil of port P enters four oil inlet grooves 54 through an oil inlet hole 52 and a third oil inlet hole 52a, two of the oil inlet grooves 54 are covered by the intermediate disk 103, the other two oil inlet grooves 54 enter the meshing cavity 2a through a distributing hole, two of the variable oil grooves 55 are communicated with the distributing hole, the other two variable oil grooves 55 are covered by the intermediate disk 103, if the variable rotary disk 6 is at a high-pressure working position, the meshing cavity 2a communicated with the two variable oil grooves 55 is communicated with port T, and the hydraulic motor has two meshing cavities 2a communicated with port P and is in a small-displacement working state; if the variable capacity rotary table 6 is at the initial working position, the meshing cavity 2a communicated with the two variable capacity oil grooves 55 is communicated with the port P, and the hydraulic motor has four meshing cavities 2a communicated with the port P and is in a large-displacement working state. The hydraulic oil of P mouth gets into meshing chamber 2a through valve plate 5 after, acts on rotor 2, promotes rotor 2 rotatory, and then drives valve plate 5 rotatory through left-hand linkage 4, realizes distributing through sixteen oil grooves that the pressure that the flow changes nine meshing chambers 2a realizes hydraulic motor's continuous distribution to realize hydraulic motor's continuous rotation and moment of torsion and are exported by output shaft 9.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the technical principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.

Claims

1. The utility model provides a dish distribution flow hydraulic motor, includes stator and rotor, be equipped with in the stator and control the commentaries on classics hole that runs through, its characterized in that: the stator is fixedly provided with a middle disc at the left end of the rotating hole, and a connecting disc at the right end; the right end of the connecting disc is fixedly provided with a right end cover, an output shaft is rotatably connected in the right end cover, the left end of the middle disc is fixedly provided with a valve block, a rotary groove is formed in the end face, facing the middle disc, of the valve block, and a valve plate is rotatably connected in the rotary groove; the left end of the valve block is provided with a P port and a T port; the inner side wall of the rotating hole is uniformly provided with a plurality of needle teeth at intervals along the circumferential direction, the rotor is eccentrically arranged in the rotating hole and is in contact with the plurality of needle teeth, and the rotor is synchronously and rotatably connected with the valve plate and the output shaft; a plurality of meshing cavities between the middle disc and the connecting disc are formed in the rotary hole between the rotor and the plurality of needle teeth;

2. The disc-split hydraulic motor according to claim 1, wherein: the variable control assembly comprises an annular variable turntable, the left end of the valve plate is provided with a left annular groove, and the variable turntable is rotatably connected in the left annular groove; an arc-shaped groove is formed in the right end of the left annular groove in the valve plate, a baffle plate extending into the arc-shaped groove is arranged at the right end of the variable rotary plate, a control cavity communicated with the P port is formed between the baffle plate and one end of the arc-shaped groove in the arc-shaped groove, a cavity communicated with the T port is formed between the baffle plate and the other end of the arc-shaped groove, and a variable torsion spring for forcing the variable rotary plate to drive the baffle plate to move towards the direction of the compression control cavity is arranged at the left end of the rotary groove in the valve block; the set pressure of the variable control component is the pressure set by the variable torsion spring; the right end of the variable rotary table is provided with a first annular groove communicated with the variable oil groove, when the oil pressure of the port P is greater than the set pressure of the variable torsion spring, the variable rotary table is rotated to a high-pressure working position, and the first annular groove is communicated with the port T; when the oil pressure of the port P is smaller than the set pressure of the variable torsion spring, the variable turntable rotates to the initial working position, and the first annular groove is communicated with the port P.

3. The disc-split hydraulic motor according to claim 2, wherein: an oil inlet hole communicated with the port P is axially formed in the valve plate; a first oil return hole and a first oil inlet hole which are communicated with the first ring groove are formed in the variable rotary table; a second oil return hole communicated with the oil return groove and a second oil inlet hole communicated with the oil inlet hole are formed in the valve plate; when the variable turntable is rotated to a high-pressure working position, the first oil return hole is communicated with the second oil return hole, and the first oil inlet hole is disconnected with the second oil inlet hole; when the variable turntable rotates to the initial working position, the first oil return hole is disconnected with the second oil return hole, and the first oil inlet hole is communicated with the second oil inlet hole.

4. The disc-split hydraulic motor according to claim 3, wherein: and a third oil inlet hole used for communicating the oil inlet groove and the oil inlet hole and a variable oil hole used for communicating the variable oil groove and the first ring groove are arranged in the valve plate.

5. The disc-split hydraulic motor according to claim 3, wherein: and a third oil return hole for communicating the cavity with one of the oil return grooves and a fourth oil inlet hole for communicating the control cavity with the oil inlet hole are formed in the valve plate.

6. The disc-split hydraulic motor according to claim 2, wherein: and an oil return ring groove for communicating the oil return grooves with the T port is formed in the left end of the valve plate.

7. The disc-split hydraulic motor according to claim 1, wherein: the rotor and the valve plate are in synchronous rotating connection through a left linkage shaft, and the rotor and the output shaft are in synchronous rotating connection through a right linkage shaft.

8. The disc-split hydraulic motor according to claim 1, wherein: the number of the meshing cavities and the number of the through holes are nine; the number of the oil inlet grooves and the number of the variable oil grooves are four; the number of the oil return grooves is eight.