CN112177843A - Inner curve radial plunger hydraulic motor - Google Patents
Inner curve radial plunger hydraulic motor Download PDFInfo
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- CN112177843A CN112177843A CN202011068690.6A CN202011068690A CN112177843A CN 112177843 A CN112177843 A CN 112177843A CN 202011068690 A CN202011068690 A CN 202011068690A CN 112177843 A CN112177843 A CN 112177843A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
- F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
- F03C1/0447—Controlling
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
Abstract
The invention discloses an inner curve radial plunger hydraulic motor which comprises a shell, a first rotor assembly, a second rotor assembly and a variable control assembly, wherein the first rotor assembly, the second rotor assembly and the variable control assembly are arranged in the shell; the first rotor assembly comprises a first rotating disc, the second rotor assembly comprises a second rotating disc, an output shaft extends from the right side of the second rotating disc, the variable control assembly comprises a variable spring, a left annular groove is formed in the outer side of the convex shaft, a convex ring is arranged on the left side of the first rotating disc, and a control cavity communicated with the port P is formed in the left annular groove; the variable spring is positioned between the first rotating disc and the positioning ring; the first rotary disc is provided with a first radial hole along the circumferential direction, and the second rotary disc is internally provided with a second radial hole along the circumferential direction; the hydraulic motor has a simple structure, and can automatically adjust the rotating speed and the torque.
Description
Technical Field
The invention belongs to the technical field of hydraulic motors, and particularly relates to an inner curve radial plunger hydraulic motor.
Background
An inner curve radial plunger type hydraulic motor is a low-speed large-torque hydraulic motor frequently selected in the industries of engineering machinery, mine equipment and the like. Because the hydraulic motor plunger does work repeatedly in each rotation, the working volume of single-circle rotation is larger, and the number of the plungers is larger, so that the working stress state of each plunger can be effectively dispersed, and the hydraulic motor plunger has stronger impact resistance and high pressure resistance.
The inner side surfaces of stators of the existing inner curve radial plunger type hydraulic motors are all wavy curved surfaces, the curved surfaces are formed by connecting a plurality of independent concave arc surfaces end to end, for example, the invention with the Chinese patent number of 201010197277.X, which is named as an invention patent of an 'inner curve multi-action radial plunger type hydraulic motor', the inner side surfaces of the used stators are formed by 8 independent and communicated concave arc surfaces, the displacement of the inner curve radial plunger type hydraulic motor in the prior art is fixed, and if the displacement value after the displacement is changed, the structure of the motor needs to be integrally changed, for example, the structure of an oil distribution shaft and a rotor is changed, so that the oil distribution shaft can input oil with other proportions or the quantity of oil inlet plungers is changed, the structure is complex, the cost is high, and the change of the displacement value is not facilitated 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 an inner curve radial plunger hydraulic 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 an inner curve radial plunger hydraulic motor which comprises a shell, a first rotor assembly, a second rotor assembly and a variable control assembly, wherein the first rotor assembly, the second rotor assembly and the variable control assembly are arranged in the shell; the variable control assembly comprises a variable spring, a left annular groove is formed in the outer side, close to the left end cover, of the protruding shaft, a protruding ring extending into the left annular groove is arranged on the left side of the first rotary disc, and a control cavity communicated with the port P is formed between the left end of the protruding ring and the left end of the left annular groove in the left annular groove; the variable spring is positioned between the first rotating disc and the positioning ring and used for forcing the first rotating disc to move leftwards; a plurality of first radial holes are uniformly formed in the first rotary disc at intervals along the circumferential direction, and a plurality of second radial holes are uniformly formed in the second rotary disc at intervals along the circumferential direction; when the pressure of the port P is lower than the set pressure of the variable spring, the first rotary disc moves leftwards to be separated from the second rotary disc, the port P is disconnected with the first radial hole, when the pressure of the port P exceeds the set pressure of the variable spring, the second rotary disc moves rightwards to be connected with the second rotary disc, and the port P can be communicated with the first radial hole.
Through the technical scheme, when the inner curve radial plunger hydraulic motor works, when the oil pressure of the port P is lower than the set pressure of the variable spring, the first rotary disc is abutted against the left end cover under the action of the variable spring, the first rotary disc is separated from the second rotary disc, and the port P is disconnected with the first radial hole, so that the first rotor assembly cannot run, oil at the port P enters the second radial holes in sequence at the moment, the second rotor assembly drives the output shaft to run at a high speed after running, and the torque output by the output shaft is smaller because the input pressure of the port P is smaller; when the oil pressure of P mouth is greater than during the pressure that variable spring set for, P mouth fluid gets into and promotes first carousel right motion in the control chamber, makes first carousel and second carousel be connected, and P mouth fluid can get into a plurality of first radial holes in proper order this moment, thereby makes first rotor subassembly with the second rotor subassembly moves simultaneously, thereby transmits the moment of torsion to on the output shaft, the rotational speed of output shaft is lower, because P mouth oil pressure is great, and the great moment of torsion can be exported to the output shaft.
Furthermore, the variable control assembly further comprises a return spring, a plurality of spring grooves are uniformly arranged on the right end face of the first rotary disc at intervals along the circumferential direction of the protruding shaft, a positioning column is connected in each spring groove in a sliding manner, the return spring is installed between the positioning column and the spring grooves and used for forcing the positioning column to move rightwards, a plurality of positioning holes are uniformly arranged on the left end face of the second rotary disc at intervals along the circumferential direction of the protruding shaft, when the positioning columns are inserted into the positioning holes, the first rotary disc is connected with the second rotary disc, and when the positioning columns are separated from the positioning holes, the first rotary disc is separated from the second rotary disc; when the first rotary disc moves rightwards, the first rotary disc can push the positioning column to slide, the reset spring is extruded at the moment, the positioning column is abutted against the left end face of the second rotary disc, when the positioning column is opposite to the positioning hole, the positioning column is inserted into the positioning hole, and the first rotary disc is connected with the second rotary disc.
Furthermore, a first oil hole communicated with the P port and a second oil hole communicated with the T port are axially arranged in the protruding shaft, and a third oil hole used for communicating the first oil hole with the control cavity is arranged in the protruding shaft.
Furthermore, a flow distribution shaft is fixedly arranged in the convex shaft along the axial direction, and an inner curved surface is arranged on the side surface of the inner cavity of the shell; the first rotor assembly further comprises a first plunger, a plurality of first radial piston holes which are in one-to-one correspondence with the first radial holes are uniformly arranged on the outer side of the circumference of the first rotary disc at intervals along the circumferential direction, the first plungers are connected in the first radial piston holes in a sliding mode respectively, and a first rolling ball which is in contact with the inner curved surface is arranged at the far end of each first plunger; a plurality of first radial oil inlet holes communicated with the first oil inlet ring groove and first radial oil return holes communicated with the first oil return ring groove are uniformly arranged in the convex shaft at intervals along the circumferential direction, one of the first radial oil inlet holes is communicated with the first oil hole, and one of the first radial oil return holes is communicated with the second oil hole; the circumference outside of protruding axle is equipped with first oil feed tank in every first radial oil feed port department, and is equipped with first oil return groove in every first radial oil return port department, first oil feed tank and first oil return groove are crisscross the setting in proper order along the axial of protruding axle, and when P mouthful pressure is less than the settlement pressure of variable spring, first carousel moves left, and first radial hole cuts off not logical with first oil feed tank, and when P mouthful pressure exceeded the settlement pressure of variable spring, first carousel moves right and makes first radial hole and first oil feed tank be located same axis distance, first radial hole can communicate with first oil feed tank.
Through the technical scheme, oil at the P port enters the first oil inlet groove through the first oil hole, the first radial oil inlet hole and the first oil inlet ring groove, the first oil inlet groove enters the first radial piston hole through the first radial hole to act on the first plunger, the first rotary disc is pushed to rotate along the inner curve, and when the first plunger moves to the convex part of the inner curve, the corresponding first radial piston hole is communicated with the T sub-assembly through the first radial hole, the first oil return groove, the first radial oil return hole, the first oil return ring groove and the second oil hole, so that the first rotor assembly is driven to rotate.
Furthermore, the second rotor assembly further comprises a second plunger, a plurality of second radial piston holes which are in one-to-one correspondence with the second radial holes are uniformly arranged on the outer side of the circumference of the second rotating disc at intervals along the circumferential direction, the second plungers are a plurality of and are respectively connected in the second radial piston holes in a sliding manner, and a second rolling ball which is in contact with the inner curved surface is arranged at the far end of each second plunger; a second oil inlet ring groove and a second oil return ring groove are formed in the outer side of the flow distribution shaft, a plurality of second radial oil inlet holes communicated with the second oil inlet ring groove and second radial oil return holes communicated with the second oil return ring groove are uniformly formed in the convex shaft at intervals along the circumferential direction, one of the second radial oil inlet holes is communicated with the first oil hole, and one of the second radial oil return holes is communicated with the second oil hole; and a second oil inlet groove is formed in each second radial oil inlet hole on the outer side of the circumference of the convex shaft, a second oil return groove is formed in each second radial oil return hole, and the second oil inlet grooves and the second oil return grooves are sequentially arranged in a staggered mode along the axial direction of the convex shaft.
Through the technical scheme, oil at the P port enters the second oil inlet groove through the first oil hole, the second radial oil inlet hole and the second oil inlet ring groove, the second oil inlet groove enters the second radial piston hole through the second radial hole to act on the second plunger, the second rotary table is pushed to rotate along the inner curve, and when the second plunger moves to the convex part of the inner curve, the corresponding second radial piston hole is communicated with the T port through the second radial hole, the second oil return groove, the second radial oil return hole, the second oil return ring groove and the second oil hole, so that the second rotor assembly is driven to rotate.
Advantageous effects
Compared with the prior art, the technical scheme of the invention has the following advantages:
1. when the pressure of the P port is lower than the pressure set by the variable spring, the variable control assembly controls the second rotor assembly to be disconnected with the first rotor assembly, the first oil inlet ring groove of the first rotor assembly is disconnected with the P port, and only the second rotor assembly is in a working state, so that high-speed output in light load, namely high-speed small torque, can be realized; when the pressure of the P port is greater than the pressure set by the variable spring, the variable control assembly controls the second rotor assembly to be connected with the first rotor assembly, the first oil inlet ring groove of the first rotor assembly is communicated with the P port, the first rotor assembly and the second rotor assembly are in a working state at the same time, and low speed, namely low-speed and high torque during heavy load can be realized;
2. when the pressure of the port P does not reach the pressure set by the variable spring, the first rotor assembly does not work, no friction exists between the first rotor assembly and the shell, and the service life can be prolonged;
3. the invention has simple and reasonable structure, compact volume and low manufacturing cost.
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, in a low speed, high torque operating condition;
fig. 3 is a sectional view taken along the direction a-a in fig. 1, and is in a high-speed low-torque operation state.
Detailed Description
Referring to fig. 1-3, the present invention provides an inner curve radial plunger hydraulic motor, including a housing 1, and a first rotor assembly, a second rotor assembly and a variable control assembly installed in the housing 1, wherein a left end cover 11 is installed at a left end of the housing 1, a right end cover 12 is installed at a right end of the housing 1, a protruding shaft 4 extending to the right end cover 12 is installed on the left end cover 11, a P port and a T port are installed at a left end of the protruding shaft 4, an inner cavity 1a of the housing 1 is communicated with the T port, and a positioning ring 4a is fixedly installed at an outer side of a circumference of the protruding shaft 4; the first rotor component comprises a first rotating disc 6 which is rotatably connected to the protruding shaft 4 and located on the left side of the positioning ring 4a, the second rotor component comprises a second rotating disc 3 which is rotatably connected to the protruding shaft 4 and located on the right side of the positioning ring 4a, the right side of the second rotating disc 3 is provided with an output shaft 3a extending out of the right end cover 12 in an extending mode, the variable control component comprises a variable spring 60, the protruding shaft 4 is provided with a left annular groove 4b on the outer side close to the left end cover 11, the left side of the first rotating disc 6 is provided with a protruding ring 66 extending into the left annular groove 4b, and a control cavity 6b communicated with the port P is formed between the left end of the protruding ring 66 and the left end of the left annular groove 4b in the left annular; the variable spring 60 is positioned between the first rotating disk 6 and the positioning ring 4a and is used for forcing the first rotating disk 6 to move leftwards; a plurality of first radial holes 62 are uniformly formed in the first rotary disc 6 at intervals along the circumferential direction, and a plurality of second radial holes 31 are uniformly formed in the second rotary disc 3 at intervals along the circumferential direction; when the pressure of the port P is lower than the set pressure of the variable spring 60, the first rotary disk 6 moves leftwards to be separated from the second rotary disk 3, the port P is disconnected from the first radial hole 62, when the pressure of the port P exceeds the set pressure of the variable spring 60, the second rotary disk 3 moves rightwards to be connected with the second rotary disk 3, and the port P can be communicated with the first radial hole 62.
The variable control assembly further comprises a return spring 81, a plurality of spring grooves 67 are uniformly formed in the right end face of the first rotary disc 6 at intervals along the circumferential direction of the protruding shaft 4, a positioning column 82 is connected to each spring groove 67 in a sliding manner, the return spring 81 is installed between the positioning column 82 and the spring groove 67 and used for forcing the positioning column 82 to move rightwards, a plurality of positioning holes 30 are uniformly formed in the left end face of the second rotary disc 3 at intervals along the circumferential direction of the protruding shaft 4, when the positioning columns 82 are inserted into the positioning holes 30, the first rotary disc 6 is connected with the second rotary disc 3, and when the positioning columns 82 are separated from the positioning holes 30, the first rotary disc 6 is separated from the second rotary disc 3; when the first rotary table 6 moves rightwards, the first rotary table 6 pushes the positioning column 82 to slide, at the moment, the return spring 81 is pressed to enable the positioning column 82 to abut against the left end face of the second rotary table 3, when the positioning column 82 is opposite to the positioning hole 30, the positioning column 82 is inserted into the positioning hole 30, and the first rotary table 6 is connected with the second rotary table 3.
A first oil hole 41 communicated with the port P and a second oil hole 42 communicated with the port T are axially arranged in the protruding shaft 4, and a third oil hole 40 used for communicating the first oil hole 41 with the control cavity 6b is arranged in the protruding shaft 4. A flow distribution shaft 5 is fixedly arranged in the convex shaft 4 along the axial direction, and an inner curved surface 101 is arranged on the side surface of the inner cavity of the shell 1.
The first rotor assembly further comprises a first plunger 71, a plurality of first radial piston holes 68 corresponding to the first radial holes 62 one by one are uniformly arranged on the circumferential outer side of the first rotary table 6 at intervals along the circumferential direction, the first plungers 71 are a plurality and are respectively connected in the first radial piston holes 68 in a sliding mode, and a first rolling ball 72 in contact with the inner curved surface 101 is arranged at the far end of each first plunger 71; a first oil inlet ring groove 52 and a first oil return ring groove 51 are arranged on the outer side of the flow distribution shaft 5, a plurality of first radial oil inlet holes 4c communicated with the first oil inlet ring groove 52 and first radial oil return holes 4d communicated with the first oil return ring groove 51 are uniformly arranged in the protruding shaft 4 at intervals along the circumferential direction, one of the first radial oil inlet holes 4c is communicated with the first oil hole 41, and the other one of the first radial oil return holes 4d is communicated with the second oil hole 42; a first oil inlet groove 412 is formed in each first radial oil inlet hole 4c on the outer side of the circumference of the protruding shaft 4, a first oil return groove 422 is formed in each first radial oil return hole 4d, the first oil inlet grooves 412 and the first oil return grooves 422 are sequentially arranged in a staggered mode in the axial direction of the protruding shaft 4, when the pressure of the port P is lower than the set pressure of the variable spring 60, the first rotary disc 6 moves leftwards, the first radial hole 62 is isolated from the first oil inlet groove 412 and is not communicated with the first oil inlet groove 412, when the pressure of the port P exceeds the set pressure of the variable spring 60, the first rotary disc 6 moves rightwards to enable the first radial hole 62 and the first oil inlet groove 412 to be located on the same axial distance, and the first radial hole 62 can be communicated with the first oil inlet groove 412.
The second rotor assembly further comprises a second plunger 21, a plurality of second radial plunger holes 38 corresponding to the second radial holes 31 one by one are uniformly arranged at intervals along the circumferential direction outside the circumference of the second rotating disc 3, the second plungers 21 are a plurality and are respectively connected in the second radial plunger holes 38 in a sliding manner, and a second rolling ball 22 in contact with the inner curved surface 101 is arranged at the far end of each second plunger 21; a second oil inlet ring groove 54 and a second oil return ring groove 53 are formed in the outer side of the flow distribution shaft 5, a plurality of second radial oil inlet holes 4e communicated with the second oil inlet ring groove 54 and second radial oil return holes 4f communicated with the second oil return ring groove 53 are uniformly formed in the protruding shaft 4 at intervals along the circumferential direction, one of the second radial oil inlet holes 4e is communicated with the first oil hole 41, and one of the second radial oil return holes 4f is communicated with the second oil hole 42; the circumference outside of protruding axle 4 is equipped with second oil feed tank 411 in every radial inlet port 4e department, and is equipped with second oil gallery 421 in every radial oil gallery 4f department, second oil feed tank 411 and second oil gallery 421 are along the crisscross setting in proper order of protruding axle 4's axial.
In this embodiment, when the inner curve radial plunger hydraulic motor works, when the oil pressure of the port P is lower than the pressure set by the variable spring 60, the first rotary disk 6 abuts against the left end cover 11 under the action of the variable spring 60, the first rotary disk 6 is separated from the second rotary disk 3, and the port P is disconnected from the first radial hole 62, so that the first rotor assembly cannot operate, at this time, the oil of the port P enters the second oil inlet slot 411 through the first oil hole 41, the second radial oil inlet hole 4e and the second oil inlet ring groove 54, enters the second radial piston hole 38 through the second radial hole 31 from the second oil inlet slot 411 to act on the second plunger 21, and pushes the second rotary disk 3 to rotate along the inner curve, and when the second plunger 21 moves to the convex portion of the inner curve, the corresponding second radial piston hole 38 passes through the second radial hole 31, the second oil return groove 421, the second radial oil return hole 4f, the second oil return ring groove 53, The second oil hole 42 is communicated with the T port, so that the second rotor assembly is driven to rotate, the output shaft 3a is driven to run at a high speed after the second rotor assembly runs, and the torque output by the output shaft 3a is small due to the fact that the input pressure of the P port is small.
When the oil pressure of the port P is greater than the pressure set by the variable spring 60, the oil in the port P enters the control chamber 6b to push the first rotary disk 6 to move rightwards, the first rotary disk 6 drives the positioning column 82 to abut against the left end face of the second rotary disk 3, when the positioning column 82 is over against the positioning hole 30, the positioning column 82 is inserted into the positioning hole 30, the first rotary disk 6 is connected with the second rotary disk 3, and simultaneously, when the first rotary disk 6 moves rightwards, the first radial hole 62 and the first oil inlet groove 412 are located at the same axial distance, the first radial hole 62 can be communicated with the first oil inlet groove 412, the oil in the port P enters the first oil inlet groove 412 through the first oil hole 41, the first radial oil inlet hole 4c and the first oil inlet ring groove 52, enters the first radial piston hole 68 through the first radial hole 62 from the first oil inlet groove 412 to act on the first plunger 71 to push the first rotary disk 6 to rotate along the inner curve, when the first plunger 71 moves to the convex part of the inner curve, the corresponding first radial piston hole 68 is communicated with the T port through the first radial hole 62, the first oil return groove 422, the first radial oil return hole 4d, the first oil return ring groove 51, the second oil hole 42, thereby driving the first rotor assembly to rotate, so that the first rotor assembly and the second rotor assembly run simultaneously, thereby transmitting the torque to the output shaft 3a, the rotating speed of the output shaft 3a is low, and the output shaft 3a can output a large torque because the oil pressure of the P port is large.
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 (5)
1. An inner curve radial piston hydraulic motor comprising a housing, and a first rotor assembly, a second rotor assembly and a variable control assembly mounted within the housing, characterized in that: the left end of the shell is provided with a left end cover, the right end of the shell is provided with a right end cover, the left end cover is provided with a convex shaft extending towards the right end cover, the left end of the convex shaft is provided with a P port and a T port, the inner cavity of the shell is communicated with the T port, and the outer side of the circumference of the convex shaft is fixedly provided with a positioning ring; the variable control assembly comprises a variable spring, a left annular groove is formed in the outer side, close to the left end cover, of the protruding shaft, a protruding ring extending into the left annular groove is arranged on the left side of the first rotary disc, and a control cavity communicated with the port P is formed between the left end of the protruding ring and the left end of the left annular groove in the left annular groove; the variable spring is positioned between the first rotating disc and the positioning ring and used for forcing the first rotating disc to move leftwards; a plurality of first radial holes are uniformly formed in the first rotary disc at intervals along the circumferential direction, and a plurality of second radial holes are uniformly formed in the second rotary disc at intervals along the circumferential direction; when the pressure of the port P is lower than the set pressure of the variable spring, the first rotary disc moves leftwards to be separated from the second rotary disc, the port P is disconnected with the first radial hole, when the pressure of the port P exceeds the set pressure of the variable spring, the second rotary disc moves rightwards to be connected with the second rotary disc, and the port P can be communicated with the first radial hole.
2. The inner curve radial ram hydraulic motor of claim 1, wherein: the variable control subassembly still includes reset spring, the right-hand member face of first carousel is equipped with a plurality of spring grooves along the circumference interval of protruding axle uniformly, and every spring inslot is equal sliding connection has the reference column, reset spring installs the reference column with be used for forcing the reference column to move right between the spring groove, the left end face of second carousel is equipped with a plurality of locating holes along the circumference interval of protruding axle uniformly, and when the reference column inserted in the locating hole, first carousel and second carousel are connected, and when the reference column broke away from the locating hole, first carousel and second carousel separation.
3. The inner curve radial ram hydraulic motor of claim 1, wherein: and a first oil hole communicated with the P port and a second oil hole communicated with the T port are axially arranged in the protruding shaft, and a third oil hole used for communicating the first oil hole with the control cavity is arranged in the protruding shaft.
4. The inner curve radial ram hydraulic motor of claim 3, wherein: a flow distribution shaft is fixedly arranged in the convex shaft along the axial direction, and an inner curved surface is arranged on the side surface of the inner cavity of the shell; the first rotor assembly further comprises a first plunger, a plurality of first radial piston holes which are in one-to-one correspondence with the first radial holes are uniformly arranged on the outer side of the circumference of the first rotary disc at intervals along the circumferential direction, the first plungers are connected in the first radial piston holes in a sliding mode respectively, and a first rolling ball which is in contact with the inner curved surface is arranged at the far end of each first plunger; a plurality of first radial oil inlet holes communicated with the first oil inlet ring grooves and first radial oil return holes communicated with the first oil return ring grooves are uniformly arranged in the convex shaft at intervals along the circumferential direction; a first oil inlet groove is formed in each first radial oil inlet hole in the circumferential outer side of the convex shaft, a first oil return groove is formed in each first radial oil return hole, and the first oil inlet grooves and the first oil return grooves are sequentially arranged in a staggered mode along the axial direction of the convex shaft; when the pressure of the port P is lower than the set pressure of the variable spring, the first rotary disc moves leftwards, the first radial hole is isolated from the first oil inlet groove, when the pressure of the port P exceeds the set pressure of the variable spring, the first rotary disc moves rightwards to enable the first radial hole and the first oil inlet groove to be located on the same axial distance, and the first radial hole can be communicated with the first oil inlet groove.
5. The inner curve radial ram hydraulic motor of claim 4, wherein: the second rotor assembly further comprises a second plunger, a plurality of second radial piston holes which are in one-to-one correspondence with the second radial holes are uniformly formed in the circumferential outer side of the second rotating disc at intervals along the circumferential direction, the second plungers are in a plurality and are respectively connected in the second radial piston holes in a sliding mode, and a second rolling ball which is in contact with the inner curved surface is arranged at the far end of each second plunger; a second oil inlet ring groove and a second oil return ring groove are formed in the outer side of the flow distribution shaft, and a plurality of second radial oil inlet holes communicated with the second oil inlet ring groove and second radial oil return holes communicated with the second oil return ring groove are uniformly formed in the convex shaft at intervals along the circumferential direction; and a second oil inlet groove is formed in each second radial oil inlet hole on the outer side of the circumference of the convex shaft, a second oil return groove is formed in each second radial oil return hole, and the second oil inlet grooves and the second oil return grooves are sequentially arranged in a staggered mode along the axial direction of the convex shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011068690.6A CN112177843B (en) | 2020-10-09 | 2020-10-09 | Inner curve radial plunger hydraulic motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011068690.6A CN112177843B (en) | 2020-10-09 | 2020-10-09 | Inner curve radial plunger hydraulic motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112177843A true CN112177843A (en) | 2021-01-05 |
| CN112177843B CN112177843B (en) | 2023-05-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011068690.6A Active CN112177843B (en) | 2020-10-09 | 2020-10-09 | Inner curve radial plunger hydraulic motor |
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| CN106014901A (en) * | 2016-06-21 | 2016-10-12 | 西安交通大学 | Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston |
| CN209385283U (en) * | 2019-01-11 | 2019-09-13 | 河北派一液压机械有限公司 | A kind of walking double speed hydraulic motor device |
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2020
- 2020-10-09 CN CN202011068690.6A patent/CN112177843B/en active Active
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| US5079994A (en) * | 1989-06-08 | 1992-01-14 | Vickers Systems Gmbh | Radial piston machine |
| US6086347A (en) * | 1998-08-25 | 2000-07-11 | Thermo King Corporation | Two-stage rotary vane motor |
| EP2436918A1 (en) * | 2010-09-29 | 2012-04-04 | Salzgitter Maschinenbau AG, | Hydraulic radial piston motor |
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| CN104234965A (en) * | 2014-09-03 | 2014-12-24 | 西安交通大学 | Permanent magnet disc-type motor driven integrated radial plunger pump with double columns of plungers |
| CN106014901A (en) * | 2016-06-21 | 2016-10-12 | 西安交通大学 | Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston |
| CN209385283U (en) * | 2019-01-11 | 2019-09-13 | 河北派一液压机械有限公司 | A kind of walking double speed hydraulic motor device |
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|---|---|
| CN112177843B (en) | 2023-05-16 |
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