CN112177843B - Inner curve radial plunger hydraulic motor - Google Patents
Inner curve radial plunger hydraulic motor Download PDFInfo
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- CN112177843B CN112177843B CN202011068690.6A CN202011068690A CN112177843B CN 112177843 B CN112177843 B CN 112177843B CN 202011068690 A CN202011068690 A CN 202011068690A CN 112177843 B CN112177843 B CN 112177843B
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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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- 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 rotary table, the second rotor assembly comprises a second rotary table, an output shaft is arranged on the right side of the second rotary table in an extending mode, the variable control assembly comprises a variable spring, a left annular groove is arranged on the outer side of the convex shaft, a convex ring is arranged on the left side of the first rotary table, and a control cavity communicated with the P port is formed in the left annular groove; the variable spring is positioned between the first turntable and the positioning ring; the first turntable is provided with a first radial hole along the circumferential direction, and the second turntable 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
The inner curve radial plunger type hydraulic motor is a low-speed high-torque hydraulic motor which is often selected in industries such as engineering machinery, mining equipment and the like. The hydraulic motor plunger reciprocates for a plurality of times in each rotation, so the single-circle rotation has larger working volume, and the number of the plungers is more, 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 surface of the stator of the existing inner curve radial plunger hydraulic motor is a wavy curved surface, the curved surface is formed by connecting a plurality of independent inner concave cambered surfaces end to end, for example, the invention patent with the name of 201010197277.X is an invention patent of an inner curve multi-function radial plunger hydraulic motor, wherein the inner side surface of the stator is formed by 8 independent communicated inner concave cambered surfaces, the displacement of the inner curve radial plunger hydraulic motor in the prior art is fixed, and if the displacement value after the displacement is changed is required to be changed, the structure of the motor is required to be integrally changed, for example, the structure of an oil distributing shaft and a rotor is changed, so that the oil distributing shaft can input oil in other proportions or change the number of oil inlet plungers, the structure is complex, the cost is high, and the displacement value is not favorable to be 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 that the functional requirements of low-speed large torque and high-speed small torque are met.
Disclosure of Invention
The invention aims to provide an inner curve radial plunger hydraulic motor so as 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 above purpose, the present invention provides the following technical solutions:
in order to solve the technical problems, 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 first rotor assembly comprises a first rotary table which is rotationally connected to the protruding shaft and is positioned on the left side of the positioning ring, the second rotor assembly comprises a second rotary table which is rotationally connected to the protruding shaft and is positioned on the right side of the positioning ring, the right side of the second rotary table is extended to be provided with an output shaft which extends out of the right end cover, the variable control assembly comprises a variable spring, the protruding shaft is provided with a left ring groove at the outer side close to the left end cover, the left side of the first rotary table is provided with a protruding ring which extends into the left ring groove, and a control cavity which is communicated with the P port is formed between the left end of the protruding ring and the left end of the left ring groove in the left ring groove; the variable spring is positioned between the first rotary disc and the positioning ring and used for forcing the first rotary disc to move leftwards; the first turntable is uniformly provided with a plurality of first radial holes along the circumferential direction at intervals, and the second turntable is internally provided with a plurality of second radial holes along the circumferential direction at intervals; when the pressure of the P port is lower than the set pressure of the variable spring, the first rotary disk moves leftwards to be separated from the second rotary disk, the P port is disconnected from the first radial hole, when the pressure of the P port exceeds the set pressure of the variable spring, the second rotary disk moves rightwards to be connected with the second rotary disk, and the P port can be communicated with the first radial hole.
According to the technical scheme, when the inner curve radial plunger hydraulic motor works, when the oil pressure of the P port is lower than the pressure set by the variable spring, the first rotary table is abutted against the left end cover under the action of the variable spring, the first rotary table is separated from the second rotary table, and the P port is disconnected from the first radial hole, so that the first rotor assembly cannot run, and oil at the P port enters a plurality of second radial holes in sequence, so that the second rotor assembly runs and then drives the output shaft to run at a high speed; when the oil pressure of the P port is larger than the pressure set by the variable spring, the P port oil liquid enters the control cavity to push the first rotating disc to move rightwards, so that the first rotating disc is connected with the second rotating disc, and the P port oil liquid can sequentially enter a plurality of first radial holes, so that the first rotor assembly and the second rotor assembly can simultaneously operate, torque is transmitted to the output shaft, the rotating speed of the output shaft is lower, and the output shaft can output larger torque due to larger oil pressure of the P port.
Further, the variable control assembly further comprises a reset spring, wherein a plurality of spring grooves are uniformly formed in the right end face of the first turntable at intervals along the circumferential direction of the protruding shaft, a positioning column is slidably connected in each spring groove, the reset 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 formed in the left end face of the second turntable at intervals along the circumferential direction of the protruding shaft, when the positioning column is inserted into the positioning holes, the first turntable is connected with the second turntable, and when the positioning column is separated from the positioning holes, the first turntable is separated from the second turntable; when the first rotating disc moves rightwards, the first rotating disc can push the positioning column to slide, the reset spring is extruded at the moment, the positioning column is propped against the left end face of the second rotating disc, and when the positioning column is right opposite to the positioning hole, the positioning column is inserted into the positioning hole, and the first rotating disc is connected with the second rotating disc.
Further, a first oil hole communicated with the P port and a second oil hole communicated with the T port are arranged in the protruding shaft along the axial direction, and a third oil hole used for communicating the first oil hole with the control cavity is arranged in the protruding shaft.
Further, 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 plurality of first radial piston holes which are in one-to-one correspondence with the first radial holes are uniformly arranged at the outer side of the circumference of the first turntable along the circumferential direction at intervals, the plurality of first plungers are respectively connected in the first radial piston holes in a sliding manner, and a first rolling ball which is in contact with the inner curved surface is arranged at the telecentric end of each first plunger; the outer side of the flow distribution shaft is provided with a first oil inlet ring groove and a first oil return ring groove, 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 the other 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 feeding groove in every first radial inlet port department, and is equipped with first oil return groove in every first radial oil return hole department, first oil feeding groove and first oil return groove are crisscross setting in proper order along the axial of protruding axle, and when P mouth pressure was less than variable spring's settlement pressure, first rotor left motion, first radial hole and first oil feed groove cut off and do not lead to, and when P mouth pressure exceeded variable spring's settlement pressure, first rotor right motion made first radial hole and first oil feed groove be located same axis distance, first radial hole can be with first oil feed groove intercommunication.
Through the technical scheme, oil in 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 to push the first rotating disc to rotate along the inner curve, and when the first plunger moves to the protruding part of the inner curve, the corresponding first radial piston hole is communicated with the T port 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.
Further, 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 at circumferential outer sides of the second turntable along circumferential intervals, 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 distal end of each second plunger; the outer side of the flow distribution shaft is provided with a second oil inlet ring groove and a second oil return ring groove, 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 arranged 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 the other of the second radial oil return holes is communicated with the second oil hole; the circumference outside of protruding axle is equipped with the second oil inlet groove in every radial inlet port department of second, and is equipped with the second oil return groove in every radial oil return hole department of second, second oil inlet groove and second oil return groove are crisscross setting in proper order along the axial of protruding axle.
Through the technical scheme, oil in 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 piston to push the second rotary table to rotate along the inner curve, and when the second piston moves to the protruding 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, and the first oil inlet ring groove of the first rotor assembly is disconnected with the P port, so that only the second rotor assembly is in a working state, and high-speed output during light load, namely high-speed small torque, can be realized; when the pressure of the P port is larger 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, and the first oil inlet ring groove of the first rotor assembly is communicated with the P port, so that 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 P port does not reach the pressure set by the variable spring, the first rotor assembly does not work, friction is avoided 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 the direction A-A of FIG. 1, shown in a low speed, high torque operating condition;
fig. 3 is a cross-sectional view taken along the direction A-A of fig. 1, in a high speed, low torque operating condition.
Detailed Description
Referring to fig. 1-3, the invention provides an inner curve radial plunger hydraulic motor, which comprises a shell 1, 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 1, a left end cover 11 and a right end cover 12 are arranged at the left end of the shell 1, a protruding shaft 4 extending from the right end cover 12 is arranged on the left end cover 11, a P port and a T port are arranged at the left end of the protruding shaft 4, an inner cavity 1a of the shell 1 is communicated with the T port, and a positioning ring 4a is fixedly arranged at the outer side of the circumference of the protruding shaft 4; the first rotor assembly comprises a first rotary table 6 which is rotatably connected to the protruding shaft 4 and is positioned on the left side of the positioning ring 4a, the second rotor assembly comprises a second rotary table 3 which is rotatably connected to the protruding shaft 4 and is positioned on the right side of the positioning ring 4a, an output shaft 3a which extends out of the right end cover 12 is arranged on the right side of the second rotary table 3 in an extending mode, the variable control assembly 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 rotary table 6 is provided with a convex ring 66 which extends into the left annular groove 4b, and a control cavity 6b communicated with a P port is formed between the left end of the convex ring 66 and the left end of the left annular groove 4b in the left annular groove 4 b; the variable spring 60 is located between the first rotary disk 6 and the positioning ring 4a for forcing the first rotary disk 6 to move leftwards; the first turntable 6 is uniformly provided with a plurality of first radial holes 62 along the circumferential direction at intervals, and the second turntable 3 is internally provided with a plurality of second radial holes 31 along the circumferential direction at intervals; 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, and 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, wherein a plurality of spring grooves 67 are uniformly arranged on the right end surface of the first rotating disc 6 along the circumferential interval of the protruding shaft 4, a positioning column 82 is slidably connected in each spring groove 67, the return spring 81 is arranged between the positioning column 82 and the spring groove 67 and is used for forcing the positioning column 82 to move rightwards, a plurality of positioning holes 30 are uniformly arranged on the left end surface of the second rotating disc 3 along the circumferential interval of the protruding shaft 4, when the positioning column 82 is inserted into the positioning holes 30, the first rotating disc 6 is connected with the second rotating disc 3, and when the positioning column 82 is separated from the positioning holes 30, the first rotating disc 6 is separated from the second rotating disc 3; when the first rotating disc 6 moves rightwards, the first rotating disc 6 pushes the positioning column 82 to slide, the reset spring 81 is extruded to enable the positioning column 82 to abut against the left end face of the second rotating disc 3, and when the positioning column 82 faces the positioning hole 30, the positioning column 82 is inserted into the positioning hole 30, and the first rotating disc 6 is connected with the second rotating disc 3.
The inside of the protruding shaft 4 is axially provided with a first oil hole 41 communicated with the P port and a second oil hole 42 communicated with the T port, and the inside of the protruding shaft 4 is provided with a third oil hole 40 used for communicating the first oil hole 41 with the control cavity 6 b. The convex shaft 4 is internally and fixedly provided with a flow distribution shaft 5 along the axial direction, and the side surface of the inner cavity of the shell 1 is provided with an inner curved surface 101.
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 outer side of the circumference of the first rotor disk 6 at intervals along the circumferential direction, the plurality of first plungers 71 are respectively connected in the first radial piston holes 68 in a sliding manner, and a first rolling ball 72 in contact with the inner curved surface 101 is arranged at the distal end of each first plunger 71; the outer side of the flow distribution shaft 5 is provided with a first oil inlet ring groove 52 and a first oil return ring groove 51, 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 one of the first radial oil return holes 4d is communicated with the second oil hole 42; the circumference outside of the protruding shaft 4 is provided with a first oil inlet groove 412 at each first radial oil inlet hole 4c, and a first oil return groove 422 is provided at each first radial oil return hole 4d, the first oil inlet groove 412 and the first oil return groove 422 are sequentially staggered along the axial direction of the protruding shaft 4, when the pressure of the P port is lower than the set pressure of the variable spring 60, the first rotating disc 6 moves leftwards, the first radial hole 62 is blocked from the first oil inlet groove 412, when the pressure of the P port exceeds the set pressure of the variable spring 60, the first rotating 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 piston holes 38 corresponding to the second radial holes 31 one by one are uniformly arranged at intervals along the circumferential outside of the second turntable 3, the second plungers 21 are a plurality of and are respectively connected in the second radial piston holes 38 in a sliding manner, and a second rolling ball 22 contacted with the inner curved surface 101 is arranged at the distal end of each second plunger 21; the outer side of the flow distribution shaft 5 is provided with a second oil inlet ring groove 54 and a second oil return ring groove 53, 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 arranged 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 the protruding shaft 4 is provided with a second oil inlet groove 411 at each second radial oil inlet hole 4e, and is provided with a second oil return groove 421 at each second radial oil return hole 4f, and the second oil inlet grooves 411 and the second oil return grooves 421 are sequentially staggered along the axial direction of the protruding shaft 4.
In this embodiment, when the oil pressure of the P port is lower than the pressure set by the variable spring 60 during the operation of the inner curve radial plunger hydraulic motor, the first rotating disc 6 is abutted against the left end cover 11 under the action of the variable spring 60, and the P port is separated from the first radial hole 62, so that the first rotor assembly cannot operate, at this time, the oil of the P port 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 slot 54, and enters the second radial piston hole 38 through the second oil inlet slot 411 to act on the second piston 21 through the second radial hole 31, so as to push the second rotating disc 3 to rotate along the inner curve, and when the second piston 21 moves to the protruding portion of the inner curve, the corresponding second radial piston hole 38 is communicated with the T port through the second radial hole 31, the second oil return slot 421, the second radial oil return hole 4f, the second oil return slot 53, and the second oil return slot 42, thereby driving the second rotor assembly to rotate, so that the second rotor assembly drives the output shaft 3a to operate at a higher speed, and the output shaft 3a operates at a lower torque than the input shaft 3 a.
When the oil pressure of the port P is larger than the pressure set by the variable spring 60, the oil in the port P enters the control cavity 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 faces 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, simultaneously, when the first rotary disk 6 moves rightwards, the first radial hole 62 and the first oil inlet groove 412 are positioned on 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, the first oil inlet groove 412 enters the first radial piston hole 68 through the first radial hole 62 to act on the first plunger 71 to push the first rotating disc 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 port T 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 and the second oil hole 42, thereby driving the first rotor assembly to rotate, so that the first rotor assembly and the second rotor assembly are simultaneously operated, torque is transmitted to the output shaft 3a, the rotating speed of the output shaft 3a is lower, and the output shaft 3a can output larger torque due to larger oil pressure of the port P.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (2)
1. An inner curve radial plunger 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 from 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 first rotor assembly comprises a first rotary table which is rotationally connected to the protruding shaft and is positioned on the left side of the positioning ring, the second rotor assembly comprises a second rotary table which is rotationally connected to the protruding shaft and is positioned on the right side of the positioning ring, the right side of the second rotary table is extended to be provided with an output shaft which extends out of the right end cover, the variable control assembly comprises a variable spring, the protruding shaft is provided with a left ring groove at the outer side close to the left end cover, the left side of the first rotary table is provided with a protruding ring which extends into the left ring groove, and a control cavity which is communicated with the P port is formed between the left end of the protruding ring and the left end of the left ring groove in the left ring groove; the variable spring is positioned between the first rotary disc and the positioning ring and used for forcing the first rotary disc to move leftwards; the first turntable is uniformly provided with a plurality of first radial holes along the circumferential direction at intervals, and the second turntable is internally provided with a plurality of second radial holes along the circumferential direction at intervals; when the pressure of the P port is lower than the set pressure of the variable spring, the first rotary disk moves leftwards to be separated from the second rotary disk, the P port is disconnected from the first radial hole, when the pressure of the P port exceeds the set pressure of the variable spring, the second rotary disk moves rightwards to be connected with the second rotary disk, and the P port can be communicated with the first radial hole;
the variable control assembly further comprises a reset spring, wherein a plurality of spring grooves are uniformly formed in the right end face of the first rotary table along the circumferential direction of the protruding shaft at intervals, positioning columns are slidably connected in each spring groove, the reset spring is installed between the positioning columns and the spring grooves and used for forcing the positioning columns to move rightwards, a plurality of positioning holes are uniformly formed in the left end face of the second rotary table along the circumferential direction of the protruding shaft at intervals, when the positioning columns are inserted into the positioning holes, the first rotary table is connected with the second rotary table, and when the positioning columns are separated from the positioning holes, the first rotary table is separated from the second rotary table;
a first oil hole communicated with the P port and a second oil hole communicated with the T port are arranged in the protruding shaft along the axial direction, and a third oil hole used for communicating the first oil hole with the control cavity is arranged in the protruding shaft;
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 plurality of first radial piston holes which are in one-to-one correspondence with the first radial holes are uniformly arranged at the outer side of the circumference of the first turntable along the circumferential direction at intervals, the plurality of first plungers are respectively connected in the first radial piston holes in a sliding manner, and a first rolling ball which is in contact with the inner curved surface is arranged at the telecentric end of each first plunger; the outer side of the flow distribution shaft is provided with a first oil inlet ring groove and a first oil return ring groove, and 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; the circumference outer side of the convex shaft is provided with a first oil inlet groove at each first radial oil inlet hole, and a first oil return groove is arranged at each first radial oil return hole, and the first oil inlet grooves and the first oil return grooves are sequentially staggered along the axial direction of the convex shaft; when the pressure of the P port is lower than the set pressure of the variable spring, the first rotating disc moves leftwards, the first radial hole is blocked from being communicated with the first oil inlet groove, and when the pressure of the P port exceeds the set pressure of the variable spring, the first rotating 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.
2. The inner curve radial plunger hydraulic motor of claim 1, 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 arranged on the outer side of the circumference of the second turntable along the circumferential direction at intervals, the second plungers 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 distal end of each second plunger; the outer side of the flow distribution shaft is provided with a second oil inlet ring groove and a second oil return ring groove, 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 arranged in the convex shaft at intervals along the circumferential direction; the circumference outside of protruding axle is equipped with the second oil inlet groove in every radial inlet port department of second, and is equipped with the second oil return groove in every radial oil return hole department of second, second oil inlet groove and second oil return groove are crisscross setting in proper order along the axial of protruding axle.
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 CN112177843A (en) | 2021-01-05 |
| CN112177843B true CN112177843B (en) | 2023-05-16 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202011068690.6A Active CN112177843B (en) | 2020-10-09 | 2020-10-09 | Inner curve radial plunger hydraulic motor |
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Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE58906590D1 (en) * | 1989-06-08 | 1994-02-10 | Luk Fahrzeug Hydraulik | 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 |
| CN102996393B (en) * | 2012-11-30 | 2015-07-08 | 江苏大学 | Variable load multiple ultra-low speed inner curve wind energy absorbing plunger pump |
| CN103670900B (en) * | 2013-12-06 | 2016-08-24 | 宁波斯达弗液压传动有限公司 | A kind of change displacement hydraulic motor using asymmetric inner curve |
| CN104234965B (en) * | 2014-09-03 | 2016-03-02 | 西安交通大学 | A kind of permanent magnet disc motor drives the integral type radial plunger pump of biserial plunger |
| CN106014901B (en) * | 2016-06-21 | 2018-01-16 | 西安交通大学 | A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of 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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