CN112412724A - Constant-power control hydraulic single-cylinder double-variable plunger pump - Google Patents
Constant-power control hydraulic single-cylinder double-variable plunger pump Download PDFInfo
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- CN112412724A CN112412724A CN202011609201.3A CN202011609201A CN112412724A CN 112412724 A CN112412724 A CN 112412724A CN 202011609201 A CN202011609201 A CN 202011609201A CN 112412724 A CN112412724 A CN 112412724A
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- swash plate
- variable
- cylinder
- spring
- plunger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2064—Housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2078—Swash plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2078—Swash plates
- F04B1/2085—Bearings for swash plates or driving axles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
Abstract
The invention discloses a constant-power control hydraulic single-cylinder double-variable plunger pump, which comprises a pump shell, a cylinder body and a transmission shaft, wherein the cylinder body is provided with an assembly hole and a plurality of plunger cavities which surround the assembly hole and are provided with plungers, a swash plate and a variable supporting cylinder body which is in supporting fit with the top surface of the swash plate are arranged in the pump shell, one end of the swash plate extends to form a lever body, a variable spring which is elastically abutted against the lever body is arranged below the lever body in the pump shell, the variable spring utilizes spring force to push the swash plate to upwards turn by taking the variable supporting cylinder body as a fulcrum of the lever to increase the inclination angle of the swash plate, the plunger in a pressure oil area pushes the swash plate to overcome the spring force by hydraulic pressure, so that the swash plate is automatically matched with the inclination angle under. The invention has small volume, low cost and compact structure, and can automatically adjust the inclination angle of the swash plate by utilizing the interaction of the spring force and the hydraulic pressure, thereby realizing the constant power control of the pump.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a single-cylinder double-variable plunger pump with constant power control performance, and specifically relates to a constant power control hydraulic single-cylinder double-variable plunger pump.
Background
The hydraulic double-plunger pump is largely used in the excavator, but the conventional double pumps are all characterized in that two pump shafts are axially and mechanically connected, the axial distance is long, the use in an installation space which requires a compact structure in a micro excavator is not facilitated, and therefore the pumps which are generally used in the micro excavator are all compact double-variable pumps. There are two pumps mounted back-to-back and also axially side-by-side. But the control mode is that the total power variable is controlled by a special pump control valve.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a constant power control hydraulic single-cylinder double-variable plunger pump which is small in size, low in cost, compact in structure and capable of realizing a constant power control mode without a pump control valve, aiming at the current situation of the prior art.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a constant-power control hydraulic single-cylinder double-variable plunger pump comprises a cylinder body arranged in a pump shell and a transmission shaft used for driving the cylinder body to rotate, wherein the cylinder body is provided with an assembly hole for the transmission shaft to penetrate and assemble and a plurality of plunger cavities which surround the assembly hole and are provided with plungers, and a swash plate which enables the plungers to realize oil suction and oil discharge is obliquely arranged in the pump shell; the variable supporting cylinder matched with the top surface of the swash plate in a rotating supporting mode is arranged in the pump shell, a lever body is formed at one end of the swash plate in an extending mode, a variable spring which elastically abuts against the lever body is installed below the lever body in the pump shell, the variable spring pushes the swash plate to upwards overturn by using the variable supporting cylinder as a fulcrum of the lever through the spring force to increase the inclination angle of the swash plate, a plunger in a pressure oil area pushes the swash plate to overcome the spring force through hydraulic pressure, and the swash plate is automatically matched with the inclination angle under the combined action of the spring force and the hydraulic pressure when the load pressure changes so as to achieve.
In order to optimize the technical scheme, the specific measures adopted further comprise:
a limiter used for limiting the inclination angle of the swash plate is positioned and installed on the top wall in the pump shell, and the limiter comprises a left limiter positioned on the left side of the variable supporting cylinder and a right limiter positioned on the right side of the variable supporting cylinder; the left stopper is matched with the top surface of the left end of the swash plate and used for limiting the minimum inclination angle of the swash plate, and the right stopper is matched with the top surface of the lever body and used for limiting the maximum inclination angle of the swash plate.
The variable supporting cylinder is a cylinder, and a lever fulcrum of the swash plate and an indexing center of the plunger are eccentrically arranged to form a distance delta for realizing moment offset.
The center of the swash plate is provided with a long hole for the transmission shaft to pass through, coaxial arc-shaped positioning grooves are processed on the two sides of the long hole on the top surface of the swash plate, and the variable supporting cylinder is arranged in the positioning grooves in an anti-dropping and positioning manner.
The pump shell is formed by assembling an upper shell and a bottom cover; the top end of the variable spring is provided with a spring top seat, the top surface of the spring top seat is formed with a top seat ball head which is in butt joint with the lever body, the bottom surface of the lever body is formed with an arc ball bowl which is matched with the top seat ball head of the spring top seat, and the bottom end of the variable spring is pressed with a spring base.
The bottom cover is provided with a pressure regulating screw hole, a pressure regulating bolt for regulating the pre-tightening pressure of the variable spring through the jacking spring base is spirally arranged in the pressure regulating screw hole, and the pressure regulating bolt is spirally provided with a locking nut for jacking and locking the pressure regulating bolt with the bottom cover.
The cylinder body is provided with ten plunger cavities for installing the plungers around the assembly hole, the top ends of the plungers are matched with the bottom surface of the swash plate in a sliding abutting mode through the sliding shoes of the hinges, and the assembly hole is internally provided with an inner rack matched with the tooth grooves in the transmission shaft.
The bottom surface of the cylinder body is attached with an oil distribution disc used for oil distribution for oil suction and discharge of the plunger, the oil distribution disc is provided with an arc oil suction window and a kidney-shaped oil pressing window, and the oil pressing window comprises a first oil pressing window positioned on an outer arc and a second oil pressing window positioned on an inner arc.
The bottom surface of the cylinder body is formed with a waist-shaped oil port communicated with the corresponding plunger cavity, the waist-shaped oil port comprises a first waist-shaped oil port located on the outer circumference and a second waist-shaped oil port located on the inner circumference, and the first waist-shaped oil port and the second waist-shaped oil port are alternately arranged.
The transmission shaft is provided with a pre-tightening spring which is arranged in an assembly hole of the cylinder body and used for keeping a certain pressure between the cylinder body and the oil distribution disc, the upper end of the pre-tightening spring is pressed against a spring snap ring of the transmission shaft, and the lower end of the pre-tightening spring is pressed against a check ring for a hole in the assembly hole of the cylinder body through a gasket.
Compared with the prior art, the variable supporting cylinder serving as the fulcrum of the swash plate lever is arranged in the shell, so that the swash plate can be turned over by taking the variable supporting cylinder as the fulcrum to change the inclination angle of the swash plate. The larger the inclination angle of the swash plate, the larger the effective stroke of the plunger, and the larger the displacement of the pump, and vice versa. The variable spring is arranged below one end of the swash plate with the lever body, so that when the load is small, the variable spring can push the swash plate to the maximum angle position by utilizing the spring force, when the external load is gradually increased, the hydraulic pressure in a pressure oil area can generate a resultant moment on the swash plate through the plunger to counterbalance the spring moment of the variable spring, and the inclination angle of the swash plate tends to be stable until the moment balance point. One end of the single-cylinder double-variable plunger pump utilizes hydraulic pressure and the other end of the single-cylinder double-variable plunger pump utilizes spring force, and force is kept balanced after the spring force is overcome, so that the pressure angle of the swash plate, namely the automatic matching of the inclination angle is realized. The higher the pressure, the smaller the angle, the smaller the displacement, and the control similar to constant power is realized.
The invention has small volume, low cost and compact structure, and can automatically adjust the inclination angle of the swash plate by utilizing the interaction of the spring force and the hydraulic pressure, thereby realizing the constant power control of the pump.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic perspective view of a variable support column of the present invention;
FIG. 3 is a perspective view of the swash plate of the present invention;
FIG. 4 is a perspective view of the swash plate with variable support cylinders mounted thereon according to the present invention;
FIG. 5 is a schematic view of the top surface of the cylinder block of the present invention;
FIG. 6 is a schematic view showing the structure of the bottom surface of the cylinder body of the present invention;
FIG. 7 is a schematic structural view of the oil distribution pan of the present invention;
FIG. 8 is a schematic illustration of the position of the moment bias of the present invention; the position defined by the dotted line in the figure is the position where the variable support cylinder is installed;
fig. 9 is a lever diagram of the present invention for achieving constant power.
Detailed Description
Embodiments of the present invention are described in further detail below with reference to the accompanying drawings.
Fig. 1 to 9 are schematic structural views of the present invention.
Wherein the reference numerals are: the hydraulic oil pump comprises a pre-tightening spring H, a first waist-shaped oil port K1, a second waist-shaped oil port K2, an oil distribution disc P, an oil suction window P1, a first oil pressing window P2, a second oil pressing window P3, a piston shoe X, a pump shell 1, an upper shell 11, a bottom cover 12, a cylinder body 2, a mounting hole 2a, a plunger cavity 2b, an inner rack 2c, a transmission shaft 3, a plunger 4, a swash plate 5, an elongated hole 5a, a positioning groove 5b, a lever body 51, a variable supporting cylinder 6, a variable spring 7, a spring top seat 71, a top seat ball head 71a, a spring base 72, a left limiter 81, a right limiter 82, a pressure regulating bolt 9 and a locking nut 91.
As shown in the figure, the invention discloses a constant-power control hydraulic single-cylinder double-variable plunger pump which comprises a cylinder body 2 arranged in a pump shell 1 and a transmission shaft 3 used for driving the cylinder body 1 to rotate. Both ends of the transmission shaft 3 are rotatably supported in the pump housing 1 through bearings, and a fitting hole 2a through which the transmission shaft 3 is fitted and a plurality of plunger chambers 2b in which plungers 4 are installed are formed in the center of the cylinder block 2 so as to surround the fitting hole 2 a. As shown in fig. 5 and 6, an inner rack 2c is formed in the fitting hole 2a of the cylinder block 2, and a tooth groove that engages with the inner rack 2c in the fitting hole 2a is formed on the outer circumferential surface of the drive shaft 3. Therefore, the transmission shaft 3 can drive the cylinder body 2 to rotate together through the matching of the tooth grooves and the inner rack 2c, and accordingly the plunger 4 arranged in the plunger cavity 2b is driven to rotate together with the cylinder body 2. The pump housing 1 is provided with a swash plate 5 in an inclined manner, and the plunger 4 is pushed and pulled by the swash plate 5 in sliding contact with the swash plate 5 and reciprocates in the plunger cavity 2b, thereby realizing oil suction and discharge of the plunger 4. As shown in fig. 1, the present invention focuses on: be equipped with in the pump case 1 and rotate the variable support cylinder 6 that supports matched with the top surface of sloping cam plate 5, variable support cylinder 6 is a cylinder structure article that the metal material made, the one end of sloping cam plate 5 extends the shaping and has the lever body 51, lie in the below of this lever body 51 in the pump case 1 and install the variable spring 7 that the elasticity top connects this lever body 51, variable spring 7 can utilize the spring force of self to promote sloping cam plate 5 upwards to overturn with variable support cylinder 6 as the lever fulcrum of sloping cam plate 5 to increase the inclination of sloping cam plate 5. When the load of the pump is small, the spring force of the variable spring 7 can push the swash plate 5 to the maximum angular position, at which the displacement of the pump is maximum. Conversely, when the angle of the swash plate 5 is reduced, the displacement of the pump is also reduced, and the effective stroke of the plunger 4 can be changed due to the change in the inclination angle of the swash plate 5. The plunger 4 performs oil suction and discharge through reciprocating motion, the area of the plunger 4 in an oil suction state is called an oil suction area, and the area of the plunger 4 for pressurizing and discharging the sucked oil is called a pressure oil area. The key of the invention for realizing the constant power control of the pump is that the plunger 4 in the pressure oil area pushes the swash plate 5 to overcome the spring force by depending on the hydraulic pressure, so that the swash plate 5 is automatically matched with the inclination angle under the combined action of the spring force and the hydraulic pressure when the load pressure changes, thereby realizing the constant power control of the pump. That is to say, when the external load is gradually increased, the hydraulic pressure in the lower half area of the plunger in the oil pressing area generates a resultant moment to the swash plate 5 to counterbalance the moment of the spring, and the swash plate 5 tends to be stable until the moment balance point is reached. The invention adopts a method that one end is hydraulic pressure and the other end is spring force, and the force keeps balance after overcoming the spring force, thereby realizing the automatic matching of the inclination angle of the swash plate 5. The higher the pressure of the hydraulic pressure is, the smaller the angle of the swash plate 5 is, and the smaller the displacement is, so that the control of the pump approximate to constant power is realized.
In the embodiment, a stopper for limiting the inclination angle of the swash plate 5 is positioned and mounted on the top wall in the pump housing 1, the stopper is used for preventing the inclination angle of the swash plate 5 from being too large or too small, when the swash plate 5 is parallel to the top surface of the cylinder block 2, the stroke of the plunger 4 is zero, so that oil cannot be sucked and discharged, and when the inclination angle of the swash plate 5 exceeds a certain range, the plunger 5 is easy to pull and damage. The stopper of the present invention includes a left stopper 81 located on the left side of the variable support cylinder 6 and a right stopper 82 located on the right side of the variable support cylinder 6; the left stopper 81 is engaged with the top surface of the left end of the swash plate 5 for defining the minimum inclination angle of the swash plate 5, and the right stopper 82 is engaged with the top surface of the lever body 51 for defining the maximum inclination angle of the swash plate 5.
In the embodiment shown in fig. 8 and 9, the lever fulcrum of the swash plate 5 of the present invention is eccentrically disposed from the indexing center of the plunger 4 by a distance δ for achieving moment offset. The eccentric distance delta between the lever fulcrum of the swash plate 5 and the index center of the plunger 4 is offset in the direction of the lever body 51. As can be seen from fig. 9, the distance LT between the point of action of the variable spring 7G and the swash plate 5 and the index center of the plunger 4 is, and the distance L between the plunger 4 and the index center of the plunger 4 is. In the figure, Ft represents a spring force and Fp represents a hydraulic force.
In the embodiment, the center of the swash plate 5 of the present invention is provided with an elongated hole 5a through which the transmission shaft 3 passes, and coaxial circular arc positioning grooves 5b are formed on the top surface of the swash plate 5 on both sides of the elongated hole 5a, and the variable support cylinder 6 is positioned in the positioning grooves 5b in a slip-proof manner. The positioning groove 5b can prevent the variable support column 6 from rolling left and right and deviating from the designed support point position.
In the embodiment, the pump casing 1 of the present invention is assembled by the upper casing 11 and the lower cover 12. The top end of the variable spring 7 is provided with a spring top seat 71, the top surface of the spring top seat 71 is formed with a top seat ball head 71a which is in butt joint and matched with the lever body 51, the bottom surface of the lever body 51 is formed with an arc ball bowl which is matched with the top seat ball head 71a of the spring top seat 71, the top seat ball head 71a can rotate within the range limited by the arc ball bowl, and the bottom end of the variable spring 7 is also pressed with a spring base 72.
In the embodiment of the invention, the bottom cover 12 is formed with a pressure regulating screw hole, a pressure regulating bolt 9 for regulating the pre-tightening pressure of the variable spring 7 through the top pressure spring base 72 is spirally arranged in the pressure regulating screw hole, and the pressure regulating bolt 9 is spirally assembled with a locking nut 91 for locking the pressure regulating bolt 9 in top pressure with the bottom cover 12.
As shown in fig. 5, 6 and 1, the cylinder block 2 of the present invention is formed with ten plunger chambers 2b for mounting the plungers 4 around the fitting hole 2a, the top ends of the plungers 4 are slidably engaged against the bottom surface of the swash plate 5 by means of shoes X of the hinges,
in the embodiment, the bottom surface of the cylinder body 2 of the invention is attached with an oil distribution disc P for distributing oil for oil suction and discharge of the plunger, the oil distribution disc P is provided with a circular arc-shaped oil suction window P1 and a kidney-shaped oil pressing window, and the oil pressing window comprises a first oil pressing window P2 on the outer arc and a second oil pressing window P3 on the inner arc.
A waist-shaped oil port communicated with the corresponding plunger cavity 2b is formed in the bottom surface of the cylinder body 2, the waist-shaped oil port comprises a first waist-shaped oil port K1 on the outer circumference and a second waist-shaped oil port K2 on the inner circumference, and the first waist-shaped oil port K1 and the second waist-shaped oil port K2 are arranged in an alternating manner.
The transmission shaft 3 is provided with a pre-tightening spring H which is arranged in an assembly hole 2a of the cylinder body 2 and used for keeping a certain pressure between the cylinder body 2 and the oil distribution disc P, the upper end of the pre-tightening spring H is pressed against a spring snap ring of the transmission shaft 3, and the lower end of the pre-tightening spring H is pressed against a hole in the assembly hole 2a of the cylinder body 2 through a gasket by a check ring.
While the preferred embodiments of the present invention have been illustrated, various changes and modifications may be made by one skilled in the art without departing from the scope of the invention.
Claims (10)
1. A constant-power control hydraulic single-cylinder double-variable plunger pump comprises a cylinder body (2) arranged in a pump shell (1) and a transmission shaft (3) used for driving the cylinder body (1) to rotate, wherein the cylinder body (2) is provided with an assembly hole (2a) for the transmission shaft (3) to penetrate and assemble and a plurality of plunger cavities (2b) which are provided with plungers (4) and surround the assembly hole (2a), and a swash plate (5) enabling the plungers (4) to suck and discharge oil is obliquely arranged in the pump shell (1); the method is characterized in that: the variable swash plate pump is characterized in that a variable support cylinder (6) matched with a swash plate (5) in a rotating support mode is arranged in the pump shell (1), one end of the swash plate (5) extends to form a lever body (51), a variable spring (7) elastically abutted to the lever body (51) is installed below the lever body (51) in the pump shell (1), the variable spring (7) utilizes spring force to push the swash plate (5) to upwards overturn by taking the variable support cylinder (6) as a lever fulcrum of the swash plate (5) to increase the inclination angle of the swash plate (5), a plunger (4) in a pressure oil area pushes the swash plate (5) to overcome the spring force by means of hydraulic pressure, and the swash plate (5) is automatically matched with the inclination angle under the combined action of the spring force and the hydraulic pressure when the load pressure changes to realize the constant power control of the pump.
2. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 1, wherein: a stopper used for limiting the inclination angle of the swash plate (5) is positioned and mounted on the top wall in the pump shell (1), and comprises a left stopper (81) positioned on the left side of the variable supporting cylinder (6) and a right stopper (82) positioned on the right side of the variable supporting cylinder (6); the left stopper (81) is matched with the top surface of the left end of the swash plate (5) to limit the minimum inclination angle of the swash plate (5), and the right stopper (82) is matched with the top surface of the lever body (51) to limit the maximum inclination angle of the swash plate (5).
3. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 2, wherein: the variable supporting cylinder (6) is a cylinder, and a lever fulcrum of the swash plate (5) and an indexing center of the plunger (4) are eccentrically arranged to form a distance delta for realizing moment offset.
4. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 3, wherein: the center of the swash plate (5) is provided with a long hole (5a) for the transmission shaft (3) to pass through, coaxial arc-shaped positioning grooves (5b) are arranged on the top surface of the swash plate (5) and positioned at two sides of the long hole (5a), and the variable supporting cylinder (6) is arranged in the positioning grooves (5b) in an anti-dropping and positioning manner.
5. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 4, wherein: the pump shell (1) is formed by assembling an upper shell (11) and a bottom cover (12); the top end of the variable spring (7) is provided with a spring top seat (71), the top surface of the spring top seat (71) is provided with a top seat ball head (71a) which is in butt joint with the lever body (51), the bottom surface of the lever body (51) is provided with an arc ball bowl which is matched with the top seat ball head (71a) of the spring top seat (71), and the bottom end of the variable spring (7) is pressed with a spring base (72).
6. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 5, wherein: bottom (12) on the shaping have the pressure regulating screw, the spiral is installed and is adjusted variable spring (7) pretension pressure's pressure regulating bolt (9) through roof pressure spring base (72) in this pressure regulating screw, pressure regulating bolt (9) spiral be equipped with bottom (12) looks roof pressure locking nut (91) of locking pressure regulating bolt (9).
7. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 6, wherein: cylinder body (2) encircle pilot hole (2a) shaping have ten plunger chambeies (2b) that are used for installing plunger (4), the top of plunger (4) slide the top through piston shoe (X) of hinge and the bottom surface of sloping cam plate (5) and connect cooperateing, pilot hole (2a) in the shaping have with transmission shaft (3) on tooth's socket matched with internal rack (2 c).
8. The constant-power control hydraulic single-cylinder dual-variable plunger pump as claimed in claim 7, wherein: the bottom surface of the cylinder body (2) is attached with an oil distribution disc (P) used for oil distribution for oil suction and discharge of the plunger, the oil distribution disc (P) is provided with a circular arc oil suction window (P1) and a kidney-shaped oil pressing window, and the oil pressing window comprises a first oil pressing window (P2) positioned on an outer circular arc and a second oil pressing window (P3) positioned on an inner circular arc.
9. The constant power control hydraulic single cylinder dual variable plunger pump of claim 8, wherein: the bottom surface of the cylinder body (2) is formed with a waist-shaped oil port communicated with the corresponding plunger cavity (2b), the waist-shaped oil port comprises a first waist-shaped oil port (K1) positioned on the outer circumference and a second waist-shaped oil port (K2) positioned on the inner circumference, and the first waist-shaped oil port (K1) and the second waist-shaped oil port (K2) are alternately arranged.
10. The constant power control hydraulic single cylinder dual variable plunger pump of claim 9, wherein: the transmission shaft (3) is provided with a pre-tightening spring (H) which is arranged in an assembly hole (2a) of the cylinder body (2) and used for keeping a certain pressure between the cylinder body (2) and the oil distribution disc (P), the upper end of the pre-tightening spring (H) is pressed against a spring snap ring of the transmission shaft (3), and the lower end of the pre-tightening spring (H) is pressed against a check ring for a hole in the assembly hole (2a) of the cylinder body (2) through a gasket.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011609201.3A CN112412724A (en) | 2020-12-30 | 2020-12-30 | Constant-power control hydraulic single-cylinder double-variable plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011609201.3A CN112412724A (en) | 2020-12-30 | 2020-12-30 | Constant-power control hydraulic single-cylinder double-variable plunger pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112412724A true CN112412724A (en) | 2021-02-26 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011609201.3A Pending CN112412724A (en) | 2020-12-30 | 2020-12-30 | Constant-power control hydraulic single-cylinder double-variable plunger pump |
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| CN (1) | CN112412724A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113357115A (en) * | 2021-05-21 | 2021-09-07 | 浙江大学 | Digital electric control pump and variable servo control mechanism thereof |
| CN113669221A (en) * | 2021-08-30 | 2021-11-19 | 北京航空航天大学宁波创新研究院 | Load sensitive variable mechanism of variable pump and variable pump |
| CN113700624A (en) * | 2021-07-16 | 2021-11-26 | 北京中金泰达电液科技有限公司 | High-pressure high-speed axial plunger pump |
| CN115711210A (en) * | 2022-12-02 | 2023-02-24 | 青岛力克川液压机械有限公司 | Variable mechanism and plunger pump and plunger motor adopting same |
-
2020
- 2020-12-30 CN CN202011609201.3A patent/CN112412724A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113357115A (en) * | 2021-05-21 | 2021-09-07 | 浙江大学 | Digital electric control pump and variable servo control mechanism thereof |
| CN113700624A (en) * | 2021-07-16 | 2021-11-26 | 北京中金泰达电液科技有限公司 | High-pressure high-speed axial plunger pump |
| CN113669221A (en) * | 2021-08-30 | 2021-11-19 | 北京航空航天大学宁波创新研究院 | Load sensitive variable mechanism of variable pump and variable pump |
| CN115711210A (en) * | 2022-12-02 | 2023-02-24 | 青岛力克川液压机械有限公司 | Variable mechanism and plunger pump and plunger motor adopting same |
| CN115711210B (en) * | 2022-12-02 | 2023-10-13 | 青岛力克川液压机械有限公司 | Variable mechanism and plunger pump and plunger motor using variable mechanism |
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