CN112178001A

CN112178001A - Hydraulic cycloid motor

Info

Publication number: CN112178001A
Application number: CN202011067991.7A
Authority: CN
Inventors: 李玉昌; 刘希攀
Original assignee: Jinan Gaoling Machinery Technology Co ltd
Current assignee: Jinan Gaoling Machinery Technology Co ltd
Priority date: 2020-10-08
Filing date: 2020-10-08
Publication date: 2021-01-05

Abstract

The invention discloses a hydraulic cycloid motor, which comprises a stator, a rotor and a variable control assembly, wherein a rotating hole penetrating through the stator from left to right is formed in the stator, and a connecting block is fixedly arranged at the right end of the rotating hole of the stator; a shaft hole and a valve hole are formed in the connecting block; the right end cover is fixedly arranged at the right end of the valve hole of the connecting block; a flow distribution shaft is rotatably connected in the valve hole, and an output shaft extending out of the right end cover is arranged at the right end of the flow distribution shaft; the outer side of the connecting block is provided with an opening A and an opening B; a first ring groove and a second ring groove are formed in the outer side of the circumference of the flow distribution shaft; the inner side wall of the rotating hole is provided with a plurality of needle teeth, the rotor is eccentrically arranged in the rotating hole and is in contact with the needle teeth, and when the oil pressure of the port A or the port B is greater than the set pressure of the variable control assembly, the meshing cavity is enlarged; when the oil pressure at the port A and the port B is less than the set pressure of the variable control assembly, the meshing cavity is reduced; the pressure cycloid motor is simple in structure and can automatically adjust the rotating speed and the torque.

Description

Hydraulic cycloid motor

Technical Field

The invention belongs to the technical field of hydraulic motors, and particularly relates to a hydraulic cycloid 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 arranged in front of or behind the cycloid pin gear meshing pair, a shaft valve is generally arranged in front of the flow distribution mechanism for flow distribution, a plane flow distribution is arranged behind the shaft valve, and an output shaft is arranged at the other end of the cycloid pin gear meshing pair. And a rotor of the cycloidal pin gear meshing pair is meshed with an external tooth at one end of the universal driving shaft through an internal spline, and the other end of the universal driving 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. As a result, pressure liquid enters the body shell or the rear cover from the liquid inlet and then enters the 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 the 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 (also called shaft valve) is 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 continuously outputs torque.

The displacement of the cycloid hydraulic motor in the prior art is fixed, and if the displacement value after variable displacement needs to be changed, the structure of the motor is required to be integrally changed, such as the structures of an oil distribution shaft and a rotor, so that the structure is complex, the cost is high, and the variable displacement value is not favorably changed according to actual conditions. However, with the development of the mechanical industry, the hydraulic motor is also required to be capable of changing the displacement, so as to meet the functional requirements of low-speed large torque and high-speed small torque.

Disclosure of Invention

The invention aims to provide a hydraulic cycloid motor to solve the problem that the hydraulic motor in the prior art cannot automatically adjust the rotating speed and the torque.

In order to achieve the purpose, the invention provides the following technical scheme:

in order to solve the technical problem, the invention provides a hydraulic cycloid motor which comprises a stator, a rotor and a variable control assembly, wherein a rotating hole penetrating left and right is formed in the stator, a left end cover is fixedly installed at the left end of the rotating hole of the stator, and a connecting block is fixedly installed at the right end of the rotating hole of the stator; a shaft hole and a valve hole which are communicated with the rotating hole and are coaxial are sequentially arranged in the connecting block from left to right; the right end cover is fixedly arranged at the right end of the valve hole of the connecting block; a flow distribution shaft is rotatably connected in the valve hole, and an output shaft extending out of the right end cover is arranged at the right end of the flow distribution shaft; the outer side of the connecting block is provided with an opening A and an opening B; a first annular groove communicated with the port A and a second annular groove communicated with the port B are formed in the outer side of the circumference of the valve shaft;

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 port shaft; a needle tooth ring is connected to the left end of the rotor in the rotary hole in a sliding manner, a plurality of needle tooth grooves for containing the needle teeth are uniformly distributed on the side wall of the needle tooth ring along the circumferential direction, a rotor ring is sleeved on the outer side of the rotor in the shaft hole, and the rotor is connected in the rotor ring in a sliding manner along the axial direction of the shaft hole; a plurality of meshing cavities between the needle tooth ring and the rotor ring are formed in the rotary hole between the rotor and the plurality of needle teeth; the first ring groove and the second ring groove are communicated with the plurality of meshing cavities and are sequentially communicated with the plurality of meshing cavities along with the rotation of the rotor; when the oil pressure of the port A or the port B is greater than the set pressure of the variable control assembly, the meshing cavity is increased; when the oil pressure of the ports A and B is less than the set pressure of the variable control assembly, the meshing chamber is reduced.

Furthermore, the variable control assembly also comprises a variable spring and a variable ring, a third ring groove is formed in the left end of the flow distribution shaft along the axial direction of the shaft hole, the variable ring is connected in the third ring groove in a sliding mode, and the left end of the variable ring abuts against the right end of the rotor; the variable spring is positioned between the left end cover and the needle gear ring and used for pushing the rotor to move rightwards through the needle gear ring; the set pressure of the variable control assembly is the pressure set by the variable spring; a control cavity is formed between the right end of the variable ring and the right end of the third ring groove in the third ring groove; a shuttle valve is arranged in the flow distribution shaft, a first inlet of the shuttle valve is communicated with the first annular groove, a second inlet of the shuttle valve is communicated with the second annular groove, an outlet of the shuttle valve is communicated with the control cavity, and the shuttle valve is used for controlling high-pressure oil in the port A and the port B to enter the control cavity; when the oil pressure of the port A or the port B is larger than the set pressure of the variable spring, the variable ring pushes the rotor to move leftwards, the distance between the needle gear ring and the rotor ring is increased at the moment, and the meshing cavity is increased.

Furthermore, a first oil hole used for communicating a first inlet of the shuttle valve with the first ring groove, a second oil hole used for communicating a second inlet of the shuttle valve with the second ring groove, and a third oil hole used for communicating an outlet of the shuttle valve with the control cavity are arranged in the valve shaft.

Furthermore, a plurality of fourth oil holes for communicating the meshing cavity with the valve holes are uniformly arranged in the stator and the connecting block at intervals along the circumferential direction of the flow distribution shaft, a plurality of first axial grooves communicated with the first ring groove and a plurality of second axial grooves communicated with the second ring groove are arranged on the outer side of the flow distribution shaft along the circumferential direction, and the plurality of first axial grooves and the plurality of second axial grooves are arranged at intervals; when the valve shaft rotates, the first axial groove and the second axial groove are communicated with the fourth oil hole in sequence.

Furthermore, the left end of the valve hole is provided with a positioning ring, and the valve shaft is rotatably connected in the valve hole and positioned between the positioning ring and the right end cover.

Furthermore, the rotor and the port shaft are in synchronous rotating connection through a linkage shaft.

Advantageous effects

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

according to the invention, the variable ring and the variable spring are arranged, high-pressure oil at the port A or the port B acts on the variable ring, the higher the working pressure is, the larger the left displacement of the variable ring is, and further the longer the length of the meshing cavity is, the larger the displacement of the motor is, and further the variable requirements of low-speed large torque, high-speed small torque can be realized.

Drawings

FIG. 1 is a cross-sectional view of the present invention, shown in a full displacement operating position;

FIG. 2 is a cross-sectional view of the present invention, shown in a variable operating position;

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

FIG. 4 is a cross-sectional view taken along line B-B of FIG. 1;

FIG. 5 is a cross-sectional view taken along the line C-C in FIG. 1;

FIG. 6 is a three-dimensional structural view of a rotor ring according to the present invention;

FIG. 7 is a three-dimensional structural view of a port shaft according to the present invention;

fig. 8 is a three-dimensional structural view of the needle ring according to the present invention.

Detailed Description

Referring to fig. 1 to 8, the present invention provides a hydraulic gerotor motor, including a stator 1a, a rotor 5, and a variable control assembly, wherein the stator 1a is provided with a left-right through rotating hole 1a1, the stator 1a is fixedly provided with a left end cover 31 at the left end of the rotating hole 1a1, and a connecting block 1c is fixedly provided at the right end, and a gasket 1b is provided between the stator 1a and the connecting block 1 c; a shaft hole 1c1 and a valve hole 1c2 which are communicated with the rotary hole 1a1 and are coaxial are sequentially arranged in the connecting block 1c from left to right; the right end cover 1d is fixedly arranged at the right end of the valve hole 1c2 of the connecting block 1 c; a port shaft 9 is rotatably connected in the valve hole 1c2, and an output shaft 901 extending out of a right end cover 1d is arranged at the right end of the port shaft 9; the left end of the valve hole 1c2 is provided with a positioning ring 902, and the port shaft 9 is rotatably connected in the valve hole 1c2 and positioned between the positioning ring 902 and the right end cover 1 d; the outer side of the connecting block 1c is provided with an opening A and an opening B; the circumferential outer side of the port 9 is provided with a first annular groove 91 communicated with the port A and a second annular groove 92 communicated with the port B.

The inner side wall of the rotary hole 1a1 is uniformly provided with a plurality of needle teeth 4 at intervals along the circumferential direction, the rotor 5 is eccentrically arranged in the rotary hole 1a1 and is in contact with the plurality of needle teeth 4, and the rotor 5 is synchronously and rotationally connected with the port shaft 9 through a linkage shaft 6; a needle gear ring 2 is connected to the left end of the rotor 5 in the rotary hole 1a1 in a sliding manner, a plurality of needle gear grooves for accommodating the needle gears are uniformly distributed on the side wall of the needle gear ring 2 along the circumferential direction, a rotor ring 7 is sleeved on the outer side of the rotor 5 in the shaft hole 1c1, and the rotor 5 is connected in the rotor ring 7 in a sliding manner along the axial direction of the shaft hole 1c 1; a plurality of meshing cavities 5a between the needle tooth ring 2 and the rotor ring 7 are formed in the rotary hole 1a1 between the rotor 5 and the plurality of needle teeth 4, wherein a plurality of fourth oil holes 101 for communicating the meshing cavities 5a with the valve hole 1c2 are uniformly arranged in the stator 1a and the connecting block 1c at intervals along the circumferential direction of the flow distribution shaft 9, a plurality of first axial grooves 93 communicated with the first ring groove 91 and a plurality of second axial grooves 94 communicated with the second ring groove 92 are arranged on the outer side of the flow distribution shaft 9 along the circumferential direction, and a plurality of first axial grooves 93 and a plurality of second axial grooves 94 are arranged at intervals; when the port shaft 9 rotates, the first axial groove 93 and the second axial groove 94 are communicated with the fourth oil hole 101 in sequence; the first ring groove 91 and the second ring groove 92 are in communication with the plurality of meshing cavities 5a and are in communication with the plurality of meshing cavities 5a in sequence with the rotation of the rotor 5; when the oil pressure of the port A or the port B is larger than the set pressure of the variable control assembly, the meshing cavity 5a is increased; when the oil pressures of the ports a and B are smaller than the set pressure of the variable control unit, the engagement chamber 5a is reduced.

The variable control assembly further comprises a variable spring 3 and a variable ring 8, a third ring groove 80 is formed in the left end of the valve shaft 9 along the axial direction of the shaft hole 1c1, the variable ring 8 is connected in the third ring groove 80 in a sliding mode, and the left end of the variable ring 8 abuts against the right end of the rotor 5; the variable spring 3 is positioned between the left end cover 31 and the needle gear ring 2 and used for pushing the rotor 5 to move rightwards through the needle gear ring 2; the set pressure of the variable control component is the pressure set by the variable spring 3; a control cavity 81 is formed between the right end of the variable ring 8 and the right end of the third ring groove 80 in the third ring groove 80; a shuttle valve 10 is installed in the valve shaft 9, a first inlet of the shuttle valve 10 is communicated with the first annular groove 91, a second inlet of the shuttle valve 10 is communicated with the second annular groove 92, an outlet of the shuttle valve is communicated with the control cavity 81, and the shuttle valve 10 is used for controlling high-pressure oil in the port A and the port B to enter the control cavity 81; when the oil pressure of the port A or the port B is larger than the pressure set by the variable spring 3, the variable ring 8 pushes the rotor 5 to move leftwards, the distance between the needle gear ring 2 and the rotor ring 7 is increased at the moment, and the meshing cavity 5a is increased.

In the embodiment, the port A and the port B are communicated with two working oil ports of the reversing valve, when the port A takes oil, the port B returns oil, and when the port B takes oil, the port A returns oil. When the oil pressure of the port A or the port B is larger than the set pressure of the variable spring 3, the high-pressure oil in the port A and the port B enters the control cavity 81 through the shuttle valve 10 and acts on the right end of the variable ring 8 to push the variable ring 8 to move leftwards, the variable ring 8 pushes the rotor 5 to move leftwards when moving leftwards, the rotor 5 drives the needle gear ring 2 to compress the variable spring 3 leftwards, the distance between the needle gear ring 2 and the rotor ring 7 is increased at the moment, the length of the meshing cavity 5a is longer, and therefore the displacement of the hydraulic cycloid motor is increased, and the hydraulic cycloid motor is at the maximum displacement position at the moment as shown in figure 1. When the oil pressure of the port A and the port B is smaller than the set pressure of the variable spring 3, the variable spring 3 pushes the rotor 5 to move rightwards through the needle gear ring 2, the rotor 5 drives the variable ring 8 rightwards to extend into the third ring groove 80, the distance between the needle gear ring 2 and the rotor 5 is reduced at the moment, the length of the meshing cavity 5a is reduced, and therefore the displacement of the hydraulic cycloid motor is reduced.

In this embodiment, a first oil hole 9a for communicating the first inlet of the shuttle valve 10 with the first ring groove 91, a second oil hole 9b for communicating the second inlet of the shuttle valve 10 with the second ring groove 92, and a third oil hole 9c for communicating the outlet of the shuttle valve 10 with the control chamber 81 are provided in the port 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 hydraulic pressure cycloid motor, includes stator, rotor, variable control subassembly, 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 left end cover at the left end of the rotating hole, and a connecting block is fixedly arranged at the right end of the rotating hole; a shaft hole and a valve hole which are communicated with the rotating hole and are coaxial are sequentially arranged in the connecting block from left to right; the right end cover is fixedly arranged at the right end of the valve hole of the connecting block; a flow distribution shaft is rotatably connected in the valve hole, and an output shaft extending out of the right end cover is arranged at the right end of the flow distribution shaft; the outer side of the connecting block is provided with an opening A and an opening B; a first annular groove communicated with the port A and a second annular groove communicated with the port B are formed in the outer side of the circumference of the valve shaft;

2. The hydraulic gerotor motor of claim 1, further comprising: the variable control assembly further comprises a variable spring and a variable ring, a third ring groove is formed in the left end of the flow distribution shaft along the axial direction of the shaft hole, the variable ring is connected in the third ring groove in a sliding mode, and the left end of the variable ring abuts against the right end of the rotor; the variable spring is positioned between the left end cover and the needle gear ring and used for pushing the rotor to move rightwards through the needle gear ring; the set pressure of the variable control assembly is the pressure set by the variable spring; a control cavity is formed between the right end of the variable ring and the right end of the third ring groove in the third ring groove; a shuttle valve is arranged in the flow distribution shaft, a first inlet of the shuttle valve is communicated with the first annular groove, a second inlet of the shuttle valve is communicated with the second annular groove, an outlet of the shuttle valve is communicated with the control cavity, and the shuttle valve is used for controlling high-pressure oil in the port A and the port B to enter the control cavity; when the oil pressure of the port A or the port B is larger than the set pressure of the variable spring, the variable ring pushes the rotor to move leftwards, the distance between the needle gear ring and the rotor ring is increased at the moment, and the meshing cavity is increased.

3. The hydraulic gerotor motor of claim 2, further comprising: and a first oil hole for communicating a first inlet of the shuttle valve with the first ring groove, a second oil hole for communicating a second inlet of the shuttle valve with the second ring groove, and a third oil hole for communicating an outlet of the shuttle valve with the control cavity are arranged in the flow distribution shaft.

4. The hydraulic gerotor motor of claim 1, further comprising: a plurality of fourth oil holes for communicating the meshing cavity with the valve holes are uniformly formed in the stator and the connecting block at intervals along the circumferential direction of the flow distribution shaft, a plurality of first axial grooves communicated with the first ring grooves and a plurality of second axial grooves communicated with the second ring grooves are formed in the outer side of the flow distribution shaft along the circumferential direction, and the first axial grooves and the second axial grooves are arranged at intervals; when the valve shaft rotates, the first axial groove and the second axial groove are communicated with the fourth oil hole in sequence.

5. The hydraulic gerotor motor of claim 1, further comprising: the left end of the valve hole is provided with a positioning ring, and the valve shaft is rotatably connected in the valve hole and positioned between the positioning ring and the right end cover.

6. The hydraulic gerotor motor of claim 1, further comprising: the rotor and the port shaft are in synchronous rotating connection through a linkage shaft.