CN112302895A - Axial plunger pump - Google Patents
Axial plunger pump Download PDFInfo
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- CN112302895A CN112302895A CN202011338433.XA CN202011338433A CN112302895A CN 112302895 A CN112302895 A CN 112302895A CN 202011338433 A CN202011338433 A CN 202011338433A CN 112302895 A CN112302895 A CN 112302895A
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- 230000006835 compression Effects 0.000 claims description 34
- 238000007906 compression Methods 0.000 claims description 34
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 83
- 238000006073 displacement reaction Methods 0.000 description 9
- 238000007789 sealing Methods 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000036316 preload Effects 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005065 mining Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000002904 solvent Substances 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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Classifications
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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
- F04B1/2042—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
- F04B1/26—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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention discloses an axial plunger pump, which comprises a shell, a swash plate device, a plunger assembly, a rotor cylinder body and an oil distribution disc, wherein the swash plate device, the plunger assembly, the rotor cylinder body and the oil distribution disc are arranged in a shell cavity of the shell and are sequentially arranged, a variable piston hole which is obliquely arranged relative to the shell cavity and is arranged with the inner end opposite to one side of the swash plate device is arranged on the shell, the outer end of the variable piston hole extends to the outer side of the shell, and the axial plunger pump also comprises a swash plate control valve which is inserted into the variable piston hole from the outer end of the variable piston hole so as to push the swash plate device to rotate when a variable piston in the swash plate control valve. And according to different application scenes, different types of swash plate control valves are replaced, only the swash plate control valves need to be drawn out and other plug-in mounting is replaced, the operation is very convenient and simple, and the adaptability is stronger. To sum up, the axial plunger pump can effectively solve the problem that the existing plunger pump variable control unit is inconvenient to overhaul and replace.
Description
Technical Field
The invention relates to the technical field of hydraulic pumps, in particular to an axial plunger pump.
Background
In engineering machinery, plunger pumps are widely used by various hydraulic transmission systems due to the advantages of high rotating speed, high pressure, easiness in variable control and the like. With the development of technologies such as engineering machinery, mining machinery, automobile manufacturing and the like, different structural modes are proposed for the structure of the plunger pump, and the weight is increased along with the increase of the displacement and the corresponding volume, so that a plurality of adverse factors are caused, wherein the compact structure is particularly prominent at this time. Meanwhile, the requirements of proportional control, servo control, stepless speed regulation and the like are also provided for hydraulic elements of the hydraulic system. As is well known, the working conditions of main machines such as engineering machinery and mining machinery are very complex, the displacement of the conventional variable displacement plunger pump usually adopts a single control working mode, and the main machine system has high requirements on the skills of operators, so that the problems of abnormal operation and engine power waste or overload shutdown are easy to occur, and therefore, a structure integrating multiple controls into a whole can play a great role at this time. In addition, the excavator and the crane provide new requirements for energy conservation and emission reduction, and the pressure level of the main pump is increased continuously, so that larger discharge capacity is expected.
The traditional plunger pump adopts a double-piston structure, so that the volume occupied space is large, the installation is greatly inconvenient due to the overlarge axial size, the weight is heavy, and the reliability of the installation interface in use is poor. Meanwhile, the working condition of the variable pump is complex, the variable pump can adapt to different environments, namely different control modes are needed, the traditional plunger pump structure is fixed, the variable mode with multiple double pistons can not be controlled in multiple modes, and the requirement on operators is high.
In summary, how to effectively solve the problem that the existing plunger pump variable control unit is inconvenient to overhaul and replace is a problem which needs to be solved urgently by technical personnel in the field at present.
Disclosure of Invention
In view of the above, an object of the present invention is to provide an axial plunger pump, which can effectively solve the problem of inconvenience in repairing and replacing the variable control unit of the existing plunger pump.
In order to achieve the purpose, the invention provides the following technical scheme:
the utility model provides an axial plunger pump, includes the casing and packs into casing housing cavity and the swash plate device, plunger subassembly, rotor cylinder body and the branch food tray that set gradually, be provided with on the casing relatively the housing cavity slope set up and inner with the relative variable piston hole that sets up in swash plate device one side, the outer end in variable piston hole extends to the casing outside still includes the sloping cam plate control valve, the sloping cam plate control valve is followed the outer end cartridge in variable piston hole extremely in the variable piston hole, in order can promote when the variable piston in the sloping cam plate control valve removes the swash plate device rotates.
In the axial plunger pump, variable piston holes which are obliquely arranged are arranged, a required swash plate control valve is inserted in the variable piston holes, and the swash plate control valve can push a swash plate device to adjust the inclination angle by controlling the variable pistons to slide so as to adjust the working efficiency of the plunger pump. The structure mounting mode is simple and convenient, the replacement and the maintenance are very convenient, and only the swash plate control valve needs to be taken out, the whole shell does not need to be disassembled, and the structures such as the inner swash plate device and the like do not need to be disassembled. And according to different application scenes, different types of swash plate control valves are replaced, only the swash plate control valves need to be drawn out and other plug-in mounting is replaced, the operation is very convenient and simple, and the adaptability is stronger. To sum up, the axial plunger pump can effectively solve the problem that the existing plunger pump variable control unit is inconvenient to overhaul and replace.
Preferably, the rotor cylinder body is abutted against the oil distribution disc through a concave surface and a convex surface matched with the concave surface.
Preferably, one side of the rotor cylinder body, which is far away from the swash plate device, is provided with the spherical concave surface, and the oil distribution plate is correspondingly provided with the spherical convex surface.
Preferably, the swash plate device is disposed with its center being offset from the rotational axis of the rotor cylinder block.
Preferably, a compression elastic device is arranged on one side of the swash plate device far away from the rotor cylinder body to push the swash plate to increase the deflection angle, the inner end of the variable piston hole is positioned on one side of the swash plate device close to the rotor cylinder body, and a spherical part is arranged at the end part of the variable piston to be matched with a spherical groove cavity on the swash plate of the swash plate device.
Preferably, one or more of the following valves are provided outside the housing: load-sensitive control valves, constant pressure control valves, remote pressure regulating control valves, and electro-proportional pressure control valves.
Preferably, the swash plate type hydraulic pump further comprises a pressure control valve, and the swash plate control valve comprises: the high-pressure port is communicated with an oil outlet of the oil distribution disc, the electric proportional valve is used for communicating the high-pressure port to two ends of an electric proportional valve core of the electric proportional valve when located at a first control position and communicating the control port to two ends of the electric proportional valve core when located at a second control position, electromagnetic thrust is generated when an electromagnet is switched on so as to push the electric proportional valve core to be located at a second control position, the thrust of the electric proportional valve core is increased along with the increase of current, and two ends of the electric proportional valve core are switched on; a variable compression elastic device which is opposite to the pushing direction of the electro-proportional valve core and the electromagnetic pushing direction is arranged between the variable piston and the electro-proportional valve core, and a cavity between the variable piston and the electro-proportional valve core is connected with a one-way valve structure of which the control port is communicated to the cavity in a one-way manner; the pressure control valve conducts the high-pressure port and the control port when the pressure of the high-pressure port exceeds a set value, and conducts the control port to the oil return port when the pressure of the high-pressure port is lower than the set value.
Preferably, the control device further comprises a preloaded elastic device with the thrust force consistent with the electromagnetic thrust direction, so as to push the electric proportional valve core to move towards the second control position of the electric proportional valve; the electro-proportional valve further comprises an electro-proportional valve body, the electro-proportional valve element is inserted into the electro-proportional valve body, and a lifting elastic device opposite to the electromagnetic thrust direction is further arranged between the electro-proportional valve body and the electro-proportional valve element.
Preferably, an axial passage communicated with the control port is arranged in the middle of the electro-proportional valve core, a valve seat is arranged between the variable compression elastic device and the electro-proportional valve core, an opening is formed at the valve seat by the axial passage, the opening of the axial passage is closed when the valve seat and the electro-proportional valve core are abutted against each other, and the valve seat, the axial passage and the variable compression elastic device form the one-way valve structure.
Preferably, a load sensitive control valve is further included such that the high pressure port can communicate with the control port through the load sensitive valve.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic cross-sectional view of an axial piston pump according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of an end-face external structure of an axial plunger pump according to an embodiment of the present invention
FIG. 3 is a schematic structural diagram of a swash plate control valve according to an embodiment of the present invention;
fig. 4 is an oil path diagram of a swash plate control valve according to an embodiment of the present invention.
The drawings are numbered as follows:
the device comprises a shell 1, a swash plate device 2, a plunger assembly 3, a rotor cylinder body 4, an oil distribution disc 5, a main shaft 6, a rear cover assembly 7, a swash plate control valve 8, a pressure control valve 9, a load sensitive valve 10 and a return disc 11;
the variable piston 81, the variable compression elastic device 82, the valve seat 83, the electro-proportional valve core 84, the high pressure port 85, the variable elastic device 86, the control port 87, the electromagnet 88, the electro-proportional valve body 89 and the pre-load elastic device 90.
Detailed Description
The embodiment of the invention discloses an axial plunger pump which can effectively solve the problem that an existing plunger pump variable control unit is inconvenient to overhaul and replace. .
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1 to 4, fig. 1 is a schematic cross-sectional view of an axial plunger pump according to an embodiment of the present invention; FIG. 2 is a schematic structural view of the outer end surface of an axial piston pump according to an embodiment of the present invention, and FIG. 3 is a schematic structural view of a swash plate control valve according to an embodiment of the present invention; fig. 4 is an oil path diagram of a swash plate control valve according to an embodiment of the present invention.
In a specific embodiment, the present embodiment provides an axial piston pump, specifically, the axial piston pump includes a housing 1, a swash plate device 2, a piston assembly 3, a rotor cylinder 4, an oil distribution plate 5, a swash plate control valve 8, and a main shaft 6.
Wherein the swash plate device 2, the plunger assembly 3, the rotor cylinder block 4, and the oil distribution pan 5 are sequentially disposed in a housing cavity of the housing 1. And main shaft 6 inserts in casing 1 to be connected with the transmission between the rotor cylinder 4 in casing 1, generally adopts the key-type connection, so that main shaft 6 can drive rotor cylinder 4 and rotate. Wherein the plunger assembly 3 comprises a plurality of plungers, each plunger is arranged around the rotating axis of the rotor cylinder 4 and is respectively in sliding fit with each plunger cavity in the rotor cylinder 4, one side of the plunger cavity close to the oil distribution disc 5 is provided with an opening so as to extend to the oil distribution disc 5, and the opening continuously and circularly passes through the oil pumping port and the oil outlet on the oil distribution disc 5 in the rotating process of the oil distribution disc 5. One end of the plunger is inserted into the plunger cavity, the other end of the plunger is connected with the swash plate device 2, the swash plate device 2 is obliquely arranged, so that the plunger can be pushed to reciprocate in the plunger cavity in the rotating process of the rotor cylinder body 4 so as to move towards the direction far away from the oil distribution disc 5 when the rotor cylinder body rotates to the oil pumping port to pump oil, and the plunger moves towards the direction close to the oil distribution disc 5 so as to push the oil in the plunger cavity to enter the oil outlet when the rotor cylinder body rotates to the oil outlet, so that the pumping process is completed. Wherein the degree of inclination of the swash plate device 2 determines the working efficiency of the entire plunger pump. The swash plate device 2 and the plunger assembly 3 can be connected through a return disc 11 spherical hinge assembly to facilitate the push-pull force of the plunger.
Wherein one side of the housing 1 is slotted to form a housing cavity and the spindle 6 passes out of the other side of the housing 1. Wherein the swash plate device 2, the plunger assembly 3, the rotor cylinder block 4, and the oil distribution pan 5 are sequentially loaded into the housing chamber, and a rear cover assembly 7 is provided at an opening side of the housing chamber to close the housing chamber. One end of the main shaft 6 is connected with the rear cover component 7 through a bearing, and the other end of the main shaft is connected with the shell 1 through a bearing. Wherein the swash plate device 2 is sleeved on the main shaft 6 and is provided with a swash plate bearing bush which is fixedly arranged on the rotor cylinder body 4.
The variable piston 81 hole is obliquely arranged relative to the shell cavity, namely the variable piston 81 hole is obliquely arranged relative to the main shaft 6, the variable piston 81 is connected to the inner part of the shell 1 in a sliding manner, the inner end of the variable piston 81 hole is oppositely arranged relative to one side of the swash plate device 2, and the outer end of the variable piston 81 hole extends to the outer side of the shell 1, so that the swash plate control valve 8 is inserted into the variable piston 81 hole from the outer end of the variable piston 81 hole, the variable piston 81 in the swash plate control valve 8 can push the swash plate device 2 to rotate when moving, the inclination angle of the swash plate device 2 can be adjusted, and the pushing stroke of the plunger assembly 3 can be adjusted, and the whole working power can be changed. Wherein the swash plate control valve 8 is used for controlling the variable piston 81 at the front end to translate along the variable piston 81 hole by controlling the driving source, and pushing the swash plate device 2 to rotate when moving to the direction close to the swash plate device 2. Wherein the swash plate control valve 8 is, for example, an electric proportional control valve, a power valve, etc.
In the axial plunger pump, a variable piston 81 hole which is obliquely arranged is arranged, a required swash plate control valve 8 is inserted in the variable piston 81 hole, and the swash plate control valve 8 can push the swash plate device 2 to adjust the inclination angle by controlling the variable piston 81 to slide so as to adjust the working efficiency of the plunger pump. The structure mounting mode is simple and convenient, the replacement and the maintenance are very convenient, and only the swash plate control valve 8 needs to be taken out, the whole shell 1 does not need to be disassembled, and the structures of the inner swash plate device 2 and the like do not need to be disassembled. And according to the application scene difference, change different types of sloping cam plate control valve 8, only need take out, change other cartridges can, it is very convenient simple to operate for the adaptability is stronger. To sum up, the axial plunger pump can effectively solve the problem that the existing plunger pump variable control unit is inconvenient to overhaul and replace.
As mentioned above, the rotor cylinder 4 rotates, and the oil distribution plate 5 is stationary, so that the plunger cavity of the rotor cylinder 4 sequentially passes through the oil pumping port and the oil outlet on the oil distribution plate 5, and in order to make the two closely connected, one side of the rotor cylinder 4 away from the swash plate device 2 is closely attached to the side of the corresponding side of the oil distribution plate 5. A simpler scheme, the two contact through the laminating of circular plane. However, it is preferable here that the rotor cylinder 4 and the oil distribution disc 5 are abutted by a concave surface and a convex surface that fits the concave surface, i.e., two contact surfaces of the rotor cylinder 4 and the oil distribution disc 5 that face each other to be in abutting contact with each other, one of the contact surfaces being the convex surface and the other being the concave surface. Of course, the mating concave and convex surfaces should not be able to interfere with the rotation of the rotor cylinder 4. By adopting the concave flow distribution structure, the rotor cylinder body 4 can overturn due to the acting force of oil on the rotor cylinder body 4 in the operation process of the pump, the hydraulic pressure direction is changed by the concave flow distribution, the rotor is not easy to overturn, higher rotating speed capability can be realized, and the pressure level is improved from 28MPa to 32 MPa. The convex surface and the concave surface can be both conical or spherical. Specifically, a spherical concave surface may be disposed on a side of the rotor cylinder 4 away from the swash plate device 2, wherein the spherical convex surface is disposed on the oil distribution plate 5, and of course, the convex surface may be disposed on the former, and the concave surface may be disposed on the latter.
As mentioned, each plunger in the plunger assembly 3 is generally connected with the return disc 11 on the swash plate device 2 by a spherical hinge, wherein the return disc 11 is rotatably connected with the swash plate of the swash plate device 2 so as to rotate along with the plunger assembly 3. Wherein the axis of rotation between the return disc 11 and the swash plate element is the centre line of the swash plate device 2. Generally, the center line of the swash plate device 2 is at the same height as the rotation axis of the rotor cylinder 4. However, it is preferred here that the center of the swash plate device 2 is arranged offset with respect to the axis of rotation of the rotor cylinder 4. The swash plate device 2 is obliquely arranged, one side of the swash plate device inclines towards the direction close to the rotor cylinder body 4, the side is used for pushing the plunger to push out the oil body, namely the oil outlet side, the other side of the swash plate device inclines towards the direction far away from the rotor cylinder body 4, and the side is used for enabling the plunger to return to pump in the oil body, namely the oil inlet side. The swash plate device 2 is provided with certain eccentricity, so that the number of plungers on one side of the axis of the main shaft 6 is more than that on the other side, the acting force on the two sides of the swash plate device 2 is different, the swash plate device 2 of the pump has the reset trend of inclining towards the direction of a large swing angle, a reset mechanism can be omitted, and the pump is more compact.
For better control of the inclination angle of the swash plate device 2, a compression elastic device is generally included opposite to the variable piston 81, and the compression elastic device is generally a compression spring, but may be a compression elastic body. In order to better control the inclination angle of the swash plate device 2 and control the displacement, it is preferable that a compression elastic device is disposed on a side of the swash plate device 2 away from the rotor cylinder 4 to push the swash plate to increase the deflection angle, and an inner end of the variable piston 81 hole is disposed on a side of the swash plate device 2 close to the rotor cylinder 4 and opposite to the compression elastic device to push the swash plate device 2 to rotate to compress the spring, so that the inclination angle of the swash plate device 2 is smaller and the working power is reduced. For better transmission of thrust between the swash plate device 2 and the variable piston 81, it is preferable here that the end of the variable piston 81 is provided with a spherical part to cooperate with a spherical cavity on the swash plate of the swash plate device 2 to maintain surface contact at all times during rotation by spherical contact.
Further, it is also preferable that one or more of the following valves are provided outside the housing 1: load-sensitive control valves, constant pressure control valves, remote pressure regulating control valves, and electro-proportional pressure control valves. The control valve is arranged outside to facilitate the maintenance.
In particular, the axial plunger pump may be made to include a pressure control valve 9, and the variable control means may be made to include a high pressure port 85, a control port 87, an electro proportional valve, and a variable piston 81. Typically in use, wherein the high pressure port 85 communicates with the outlet of said oil distribution disc 5 to directly pick up high pressure oil from the outlet, and wherein the control port 87, in use, communicates with the return port via the pressure control valve 9.
The electro-proportional valve is used for communicating the high-pressure port 85 to two ends of the electro-proportional valve core 84 when being positioned at the first control position. That is, when the electro proportional valve spool 84 of the electro proportional valve moves to the first control position, the high pressure oil at the high pressure port 85 is caused to enter both sides of the electro proportional valve spool by the electro proportional valve spool 84, respectively. And when in the second control position, communicates the control port 87 to both ends of the electro-proportional spool 84 of the electro-proportional valve so that the oil pressure at both ends of the electro-proportional spool 84 at this time is equal to the control port 87. Specifically, the electro-proportional valve can be a two-position three-way electro-proportional valve, two ports on one side are respectively communicated with the high-pressure port 85 and the control port 87, and one port on the other side is respectively communicated with the cavities at two ends of the electro-proportional valve core 84.
The electromagnetic thrust generated when the electro-proportional valve is electromagnetically switched on is generally that the electromagnet 88 is arranged inside, and the internal switching-on current can generate the thrust which is driven outwards, namely the electromagnetic thrust, on the internal electromagnet 88. The electromagnetic thrust acts to urge the electro-proportional valve spool 84 to the second control position and increases as current increases. Under a general control condition, two ends of the electro proportional valve core 84 are conducted, so that hydraulic oil entering the two ends of the electro proportional valve core 84 cannot generate thrust for pushing the electro proportional valve core 84 to move.
And a variable compression elastic device 82 which is opposite to the pushing direction of the electro-magnetic thrust force of the electro-magnetic proportional valve core 84 is arranged between the variable piston 81 and the electro-proportional valve core 84, so that the electro-magnetic thrust force is resisted by the variable compression elastic device 82. The variable compression elastic device 82 is disposed between the variable piston 81 and the electro-proportional valve spool 84 such that both ends respectively exert forces on the variable piston 81 and the electro-proportional valve spool 84, and the forces are opposite to each other. The cavity between the variable piston 81 and the electro-proportional valve element 84 is connected to the control port 87 by a one-way valve structure that is one-way open to the cavity, so that when the oil pressure at the control port 87 is higher than the oil pressure at the cavity, the one-way valve structure is open to allow high-pressure oil to flow from the control port 87 to the cavity to act on the end of the variable piston 81 and both ends of the electro-proportional valve element.
The pressure control valve 9 conducts the high pressure port 85 and the control port 87 when the high pressure port 85 exceeds a set value, and conducts the control port 87 to the oil return port when the high pressure port 85 is lower than the set value, so that oil bodies in the control port 87 return to the oil tank. So that the pressure control valve 9 automatically opens the high pressure port 85 to the control port 87 when the pressure is high, so that the high pressure oil can be quickly guided to the cavity between the variable piston 81 and the electro proportional spool 84 through the above-mentioned check valve to act on the variable piston 81. When the oil pressure in the high-pressure port 85 is low, the control port 87 communicates with the oil return port, and the operation of the variable piston 81 is not interfered.
When the oil pressure of the high-pressure port 85 is not higher than the set value all the time, that is, the current oil pressure belongs to the normal oil pressure, the control port 87 is communicated with the oil return port through the pressure control valve 9, and at this time, the following two working states are mainly available: in the first working state, when the electro-proportional valve is not electrified or the current is very small, the electro-proportional valve is located at the first control position, the high-pressure port 85 is communicated to two ends of the spool of the electro-proportional valve, and high-pressure oil enters between the variable piston 81 and the electro-proportional valve spool 84, because the oil pressure is very high, the variable piston 81 is pushed to move so as to push the swash plate to rotate so as to overcome a return spring of the electro-proportional variable pump, so that the swing angle of the swash plate is zero, and the electro-proportional variable pump does not output high-pressure oil; in a second working state, when the electric proportional valve current is large, the electric proportional valve core 84 is pushed to move to enter a second control position, the cavity between the variable piston 81 and the electric proportional valve core 84 is communicated with an oil return port through the control port 87, oil bodies at the end part of the variable piston 81 enter the oil return port, so that thrust is not generated on the variable piston 81 any more, and at the moment, the electric proportional valve core 84 gradually increases the thrust on the variable compression elastic device 82 along with the increase of the current, and the pressure at two ends of the variable compression elastic device 82 is increased to be compressed, so that the variable piston 81 moves towards the direction close to the electric proportional valve core 84, so that the inclination angle of the swash plate is gradually increased, so that the oil output of the variable pump is increased until the maximum swing angle is reached, namely, the maximum oil output is maintained, and further flow regulation is realized. When the pressure of the high-pressure port 85 is very high, the pressure of an oil outlet of the variable pump is very high, when the pressure exceeds a set value, the pressure control valve 9 is triggered at the moment, the control port 87 is communicated with the high-pressure port 85 through the pressure control valve 9, at the moment, the high pressure can push the one-way valve structure open, so that high-pressure oil enters a cavity between the variable piston 81 and the electro-proportional valve core 84 through the one-way valve structure, at the moment, no matter the electro-proportional valve is located at the first control position or the second control position, the control port 87 is not communicated with an oil return port any more, so that the cavity between the variable piston 81 and the electro-proportional valve core 84 can be ensured to be in a high-pressure state, and the high-pressure oil can push the variable piston 81 to move in a direction away from the electro-proportional valve core 84, so as to push the swash plate swing angle.
As described above, when the electro-proportional valve is suddenly de-energized during normal operation, the electromagnetic thrust force disappears immediately at this time, and when the electromagnet 88 is in a failure state, the electro-proportional valve immediately enters the first control position, the variable displacement pump immediately drops to zero displacement, the host system stops operating instantly, and a great potential safety hazard exists for the engineering mechanical device. In this regard, it is also preferred to further include a preloaded elastic device 90 having a thrust force aligned with the direction of the electromagnetic thrust force to urge the electro-proportional valve spool 84 toward the second control position of the electro-proportional valve. So that when the electro-proportional valve is de-energized, the electro-proportional spool 84 remains at a certain height by preloading the resilient means 90 to maintain a small angle of inclination of the swash plate of the variable displacement pump, thereby ensuring a small displacement output. For convenience, the pre-load resilient device 90 may be disposed at an end of the electro-proportional valve spool 84 away from the variable piston 81, and in particular, a compression spring may be used, and in particular, the pre-load resilient device may be disposed on the electromagnet 88.
Further, in order to better control the movement of the electro-proportional valve element 84, it is preferable that the variable elastic device 86 is further included, specifically, if the electro-proportional valve element 84 is inserted into the electro-proportional valve element 89, wherein the variable elastic device 86 is further disposed between the electro-proportional valve element 89 and the electro-proportional valve element 84 in a direction opposite to the electromagnetic thrust direction. Specifically, the variable elastic device 86 may be installed at an end of the electro-proportional valve spool 84 remote from the variable piston 81. As at this end, the electro proportional valve spool 84 is provided with a shoulder, wherein the lifting elastic means 86 is a compression spring, which is fitted over the electro proportional valve spool 84, with one end abutting against the shoulder and the other end abutting against the electro proportional valve body 89.
Further, in order to facilitate the above-mentioned check valve structure, the whole of the electric proportional valve core is more compact, and it is preferable that an axial passage communicating with the control port 87 is provided in the middle of the electric proportional valve core 84, wherein a valve seat 83 is provided between the variable compression elastic device 82 and the electric proportional valve core 84, and the axial passage forms an opening at the valve seat 83, and the valve seat 83 closes the opening of the axial passage when abutting against the electric proportional valve core 84, so that the valve seat 83, the axial passage and the variable compression elastic device 82 form the above-mentioned check valve structure, and when the control port 87 is communicated with the high pressure port 85 or other reasons, so that the axial passage is in a high oil pressure state, at this time, the high oil pressure acts on the valve seat 83, and the valve seat 83 is pushed away from the opening against the acting force of the variable compression elastic device 82 on the valve seat 83, so as to form a certain opening degree, so that the high pressure oil flows from the gap between the valve seat 83 and the electric proportional valve core 84 to And (3) removing the solvent. When the oil pressure in the axial channel is smaller, the valve seat 83 is tightly attached to the valve core of the electric proportional valve under the action of the variable compression elastic device 82, the opening is closed, and the one-way valve is structurally closed. In order to make the valve seat 83 and the electric proportional valve core 84 have better fit, it is preferable that the valve seat 83 is formed with a spherical concave surface on the side facing the electric proportional valve core 84, and the end of the electric proportional valve core 84 is formed with a spherical convex surface to fit with the spherical concave surface of the valve seat 83. Wherein a post portion is provided on the valve seat 83 such that the variable compression resilient means 82 is fitted over the valve seat 83.
Specifically, in order to facilitate the arrangement of the electro-proportional valve, it is preferable that the electro-proportional valve spool 84 is in a cylindrical shape, the electro-proportional valve body 89 is provided with a high pressure port 85, an intermediate port and a control port 87 which are sequentially arranged in parallel in the extending direction of the electro-proportional valve spool 84, wherein the intermediate port is guided to both ends of the electro-proportional valve spool 84 through a passage, wherein the extending direction of the electro-proportional valve spool 84 is provided with two first annular grooves corresponding to the high pressure port 85 and two second annular grooves corresponding to the control port 87, which are arranged in parallel, so that when the electro-proportional valve spool 84 moves to the first control position, the first annular grooves can be correspondingly communicated with the intermediate port, and when the second control position is moved, the second annular grooves can be correspondingly communicated with the intermediate port. Wherein the groove bottom of the second annular groove is communicated with the axial channel through the radial channel. After the preload spring 90 is set, there is a slight gap between the second annular groove and the intermediate port, so that the electro-proportional valve core 84 has a certain opening degree, so that the variable displacement pump has a small flow output to ensure the system operation. In order to conveniently insert the electro-proportional valve body 89, a plurality of annular sealing grooves are formed in the outer side of the electro-proportional valve body 89, annular sealing rings are arranged in the annular sealing grooves, particularly, the two sides of the middle opening, the two sides of the control opening 87 and the two sides of the high-pressure opening 85 are provided with the annular sealing rings, and the end part of an insertion section of the electro-proportional valve body 89 is also correspondingly provided with the sealing rings so as to be conveniently inserted into the hole 81 of the variable piston in a sealing mode.
Furthermore, an open slot may be formed on a side of the variable piston 81 close to the electro-proportional valve core 84, wherein the variable compression elastic device 82 is installed into the open slot, one end of the variable compression elastic device abuts against a bottom of the open slot, the other end of the variable compression elastic device is sleeved on the valve seat 83, and the variable compression elastic device can compress the variable piston 81 until the variable piston abuts against an end surface of the electro-proportional valve body 89, so that a swash plate of the variable pump maintains a maximum swing angle, and the valve seat 83 is located in the open slot at this time.
And the swash plate further comprises a load-sensitive control valve, so that when the main engine is in a standby state and does not need to work in work, the high-pressure port 85 can be communicated with the control port 87 through the load-sensitive valve 10, so that pressure oil at the high-pressure port 85 enters a cavity between the variable piston 81 and the electro-proportional valve core 84 through a one-way valve structure, and the swash plate is in a small swing angle state. Specifically, the load-sensitive control valve includes a two-position three-way hydraulic control directional control valve, two oil ports on one side are respectively connected with a high-pressure port 85 and an oil return port, one oil port on the other side is communicated with the pressure control valve 9, namely, the two-position three-way hydraulic control directional control valve is connected between the pressure control valve 9 and the oil return port, when the valve core moves to a first position side, the oil return port is communicated with the pressure control valve 9, when the valve core moves to a second position side, the high-pressure port 85 is communicated with the pressure control valve 9, the first position side valve core control port 87 is communicated with the high-pressure port 85, the second position side valve core control port 87 is communicated with one side of the adjustable throttle valve on the oil path main road far from the oil outlet of the oil distribution disc 5, and the adjustable compression spring is arranged on the side, wherein one side of the adjustable throttle valve near the oil outlet of the oil distribution disc 5 is communicated with the variable pump, so that, when the magnitude is small enough, that is, small enough, the spool moves to the second position side, otherwise the spool moves to the first position side. Correspondingly, the pressure control valve 9 may also be a two-position three-way directional valve, a compression spring on one side is used to push the valve core to move to the load-sensitive valve 10 to communicate with the control port 87, and the high-pressure oil passing through the high-pressure port 85 reaches a sufficient oil pressure to push the valve core to overcome the acting force of the compression spring to move to make the high-pressure port 85 communicate with the control port 87.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. The utility model provides an axial plunger pump, includes the casing and packs into the casing housing cavity and the swash plate device, plunger subassembly, rotor cylinder body and the branch food tray that set gradually, its characterized in that, be provided with on the casing relatively the housing cavity slope set up and inner with the relative variable piston hole that sets up in swash plate device one side, the outer end in variable piston hole extends to the casing outside still includes the swash plate control valve, the swash plate control valve is followed the outer end cartridge in variable piston hole extremely in the variable piston hole, with can promote when the variable piston in the swash plate control valve removes the swash plate device rotates.
2. The axial plunger pump of claim 1, wherein the rotor cylinder abuts the oil distribution disc via a concave surface and a convex surface that mates with the concave surface.
3. The axial piston pump as recited in claim 2, wherein said rotor cylinder is provided with said concave surface of spherical shape on a side thereof remote from said swash plate device, and said oil distribution plate is correspondingly provided with said convex surface of spherical shape.
4. The axial piston pump as recited in claim 3, wherein said swash plate device is disposed eccentrically with respect to a rotational axis of said rotor cylinder block.
5. The axial piston pump as recited in claim 4, wherein a side of said swash plate device remote from said rotor cylinder block is provided with a compression elastic means for urging said swash plate to increase its deflection angle, an inner end of said variable piston hole is located at a side of said swash plate device close to said rotor cylinder block, and an end of said variable piston is provided with a ball member for engaging with a spherical groove cavity on a swash plate of said swash plate device.
6. The axial piston pump as recited in claim 5, characterized in that one or more of the following valves are provided outside the housing: load-sensitive control valves, constant pressure control valves, remote pressure regulating control valves, and electro-proportional pressure control valves.
7. The axial piston pump as recited in any one of claims 1-5, further comprising a pressure control valve, the swash plate control valve comprising: the high-pressure port is communicated with an oil outlet of the oil distribution disc, the electric proportional valve is used for communicating the high-pressure port to two ends of an electric proportional valve core of the electric proportional valve when located at a first control position and communicating the control port to two ends of the electric proportional valve core when located at a second control position, electromagnetic thrust is generated when an electromagnet is switched on so as to push the electric proportional valve core to be located at a second control position, the thrust of the electric proportional valve core is increased along with the increase of current, and two ends of the electric proportional valve core are switched on; a variable compression elastic device which is opposite to the pushing direction of the electro-proportional valve core and the electromagnetic pushing direction is arranged between the variable piston and the electro-proportional valve core, and a cavity between the variable piston and the electro-proportional valve core is connected with a one-way valve structure of which the control port is communicated to the cavity in a one-way manner; the pressure control valve conducts the high-pressure port and the control port when the pressure of the high-pressure port exceeds a set value, and conducts the control port to the oil return port when the pressure of the high-pressure port is lower than the set value.
8. The axial piston pump as recited in claim 7, further comprising a preloaded elastic device having a thrust force aligned with the electromagnetic thrust direction to urge the electro-proportional valve spool toward a second control position of the electro-proportional valve; the electro-proportional valve further comprises an electro-proportional valve body, the electro-proportional valve element is inserted into the electro-proportional valve body, and a lifting elastic device opposite to the electromagnetic thrust direction is further arranged between the electro-proportional valve body and the electro-proportional valve element.
9. The axial plunger pump of claim 8, wherein an axial passage communicating with the control port is provided in a middle portion of the electro-proportional valve element, a valve seat is provided between the variable compression resilient means and the electro-proportional valve element, the axial passage forms an opening at the valve seat, the valve seat closes the axial passage opening when abutting against the electro-proportional valve element, and the valve seat, the axial passage and the variable compression resilient means constitute the one-way valve structure.
10. The axial piston pump as recited in claim 9, further comprising a load sensitive control valve such that the high pressure port can communicate with the control port through the load sensitive valve.
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|---|---|---|---|
| CN202011338433.XA CN112302895A (en) | 2020-11-25 | 2020-11-25 | Axial plunger pump |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011338433.XA CN112302895A (en) | 2020-11-25 | 2020-11-25 | Axial plunger pump |
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| CN112302895A true CN112302895A (en) | 2021-02-02 |
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| CN202011338433.XA Pending CN112302895A (en) | 2020-11-25 | 2020-11-25 | Axial plunger pump |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113446280A (en) * | 2021-06-30 | 2021-09-28 | 北京航空航天大学宁波创新研究院 | Bidirectional differential pressure controller and hydraulic equipment |
| CN113530779A (en) * | 2021-08-20 | 2021-10-22 | 浙江苏强格液压股份有限公司 | Plunger pump variable mechanism |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6725658B1 (en) * | 1999-10-12 | 2004-04-27 | Brueninghaus Hydromatik Gmbh | Adjusting device of a swashplate piston engine |
| DE102009012560A1 (en) * | 2009-03-11 | 2010-09-16 | Robert Bosch Gmbh | Valve device for regulating device of hydrostatic piston engine, has conveyor line connection subjectable to conveying pressure of hydrostatic piston engine and connected with tank connection of valve block by flush valve |
| US20140116242A1 (en) * | 2012-10-31 | 2014-05-01 | Robert Bosch Gmbh | Adjustment apparatus for a hydrostatic piston machine, and hydrostatic piston machine having an adjustment apparatus of this kind |
| DE102013224113A1 (en) * | 2013-11-26 | 2015-05-28 | Robert Bosch Gmbh | hydraulic motor |
| CN104675653A (en) * | 2013-11-26 | 2015-06-03 | 罗伯特·博世有限公司 | Hydraulic machine of axial-piston design |
| CN109826836A (en) * | 2019-01-11 | 2019-05-31 | 徐州工业职业技术学院 | A kind of intelligent variable pump and hydraulic control system |
| CN109854471A (en) * | 2019-02-01 | 2019-06-07 | 中航力源液压股份有限公司 | The hydraulic planger pump of two grades of power control devices |
| CN110792584A (en) * | 2019-11-27 | 2020-02-14 | 力源液压（苏州）有限公司 | Multi-gear input power control system of plunger pump |
| CN110848111A (en) * | 2019-11-27 | 2020-02-28 | 力源液压（苏州）有限公司 | Plunger variable pump integrated control system |
| US20200263675A1 (en) * | 2015-12-25 | 2020-08-20 | Kawasaki Jukogyo Kabushiki Kaisha | Displacement adjusting device of swash plate pump |
| CN111691923A (en) * | 2020-06-19 | 2020-09-22 | 中航力源液压股份有限公司 | Straight-shaft type axial plunger variable motor device with constant pressure control |
| CN214424646U (en) * | 2020-11-25 | 2021-10-19 | 力源液压（苏州）有限公司 | Axial plunger pump |
-
2020
- 2020-11-25 CN CN202011338433.XA patent/CN112302895A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6725658B1 (en) * | 1999-10-12 | 2004-04-27 | Brueninghaus Hydromatik Gmbh | Adjusting device of a swashplate piston engine |
| DE102009012560A1 (en) * | 2009-03-11 | 2010-09-16 | Robert Bosch Gmbh | Valve device for regulating device of hydrostatic piston engine, has conveyor line connection subjectable to conveying pressure of hydrostatic piston engine and connected with tank connection of valve block by flush valve |
| US20140116242A1 (en) * | 2012-10-31 | 2014-05-01 | Robert Bosch Gmbh | Adjustment apparatus for a hydrostatic piston machine, and hydrostatic piston machine having an adjustment apparatus of this kind |
| DE102013224113A1 (en) * | 2013-11-26 | 2015-05-28 | Robert Bosch Gmbh | hydraulic motor |
| CN104675653A (en) * | 2013-11-26 | 2015-06-03 | 罗伯特·博世有限公司 | Hydraulic machine of axial-piston design |
| US20200263675A1 (en) * | 2015-12-25 | 2020-08-20 | Kawasaki Jukogyo Kabushiki Kaisha | Displacement adjusting device of swash plate pump |
| CN109826836A (en) * | 2019-01-11 | 2019-05-31 | 徐州工业职业技术学院 | A kind of intelligent variable pump and hydraulic control system |
| CN109854471A (en) * | 2019-02-01 | 2019-06-07 | 中航力源液压股份有限公司 | The hydraulic planger pump of two grades of power control devices |
| CN110792584A (en) * | 2019-11-27 | 2020-02-14 | 力源液压（苏州）有限公司 | Multi-gear input power control system of plunger pump |
| CN110848111A (en) * | 2019-11-27 | 2020-02-28 | 力源液压（苏州）有限公司 | Plunger variable pump integrated control system |
| CN111691923A (en) * | 2020-06-19 | 2020-09-22 | 中航力源液压股份有限公司 | Straight-shaft type axial plunger variable motor device with constant pressure control |
| CN214424646U (en) * | 2020-11-25 | 2021-10-19 | 力源液压（苏州）有限公司 | Axial plunger pump |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113446280A (en) * | 2021-06-30 | 2021-09-28 | 北京航空航天大学宁波创新研究院 | Bidirectional differential pressure controller and hydraulic equipment |
| CN113530779A (en) * | 2021-08-20 | 2021-10-22 | 浙江苏强格液压股份有限公司 | Plunger pump variable mechanism |
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