CN113530906A - Constant pressure control valve of high-flow high-pressure plunger pump - Google Patents
Constant pressure control valve of high-flow high-pressure plunger pump Download PDFInfo
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- CN113530906A CN113530906A CN202110712911.7A CN202110712911A CN113530906A CN 113530906 A CN113530906 A CN 113530906A CN 202110712911 A CN202110712911 A CN 202110712911A CN 113530906 A CN113530906 A CN 113530906A
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- 238000007789 sealing Methods 0.000 claims description 39
- 230000007704 transition Effects 0.000 claims description 19
- 230000033001 locomotion Effects 0.000 claims description 11
- 230000006835 compression Effects 0.000 claims description 10
- 238000007906 compression Methods 0.000 claims description 10
- 238000009434 installation Methods 0.000 claims description 9
- 238000003825 pressing Methods 0.000 claims description 6
- 230000004044 response Effects 0.000 abstract description 4
- 238000006073 displacement reaction Methods 0.000 description 17
- 238000013016 damping Methods 0.000 description 6
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/022—Flow-dividers; Priority valves
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Abstract
The invention discloses a constant pressure control valve of a high-flow high-pressure plunger pump, which is characterized by comprising a valve body, a mounting seat, a valve core assembly, a limiting ejector rod assembly and a pressure regulating spring assembly, wherein a main body of the pressure regulating spring assembly is positioned in the mounting seat; the high-pressure plunger pump has the advantages that the diameter of the main sliding valve core in the valve body is increased by increasing the diameter of the valve body, so that the response speed of the high-pressure plunger pump is increased, the inner valve core is arranged in the main sliding valve core, the axial thrust of the main sliding valve core under a high-pressure working condition can be reduced, and the control force of the pressure regulating spring assembly is reduced; when the diameter of the main sliding valve core is increased, the sectional area of the inner valve core is reduced, the thrust for pushing the main sliding valve core is kept unchanged, the adjusting force of the spring is small, and the appearance of the pressure regulating spring assembly is compact; when the set pressure needs to be remotely controlled and adjusted, the remote pressure control of the pressure oil introduced into the pressure regulating spring assembly can be realized only by disassembling the inner valve core in the valve core assembly.
Description
Technical Field
The invention relates to a control valve device, in particular to a constant-pressure control valve of a high-flow high-pressure plunger pump.
Background
Along with the development requirement of domestic large-scale equipment, the development requirement of the axial plunger pump to high pressure and large flow is accelerated, and the application of the high-pressure plunger pump with the discharge capacity of 500 milliliters per revolution and more than 500 milliliters per revolution is increased. Therefore, the variable control mode of the high-pressure plunger pump needs to be upgraded, the output flow control precision and the real-time response capability of the high-pressure plunger pump are improved, the indexes such as simplicity, convenience, reliability, energy conservation and noise are considered, and the requirements of a high-end hydraulic machinery matched hydraulic system on the high-pressure plunger pump are met.
The conventional variable control modes of the high-pressure plunger pump are constant-pressure variable, constant-power variable, electric proportional control variable, hydraulic control variable control and the like, wherein the constant-pressure variable is the most common control mode, and flow change can be set according to the output pressure of the high-pressure plunger pump in a rapid feeding and high-pressure slow feeding pressure maintaining system; along with the increase of the displacement of the high-pressure plunger pump per revolution, the diameter of the pressure oil cylinder is correspondingly increased, the flow of the pressure oil is correspondingly increased for ensuring the variable response speed of the high-pressure plunger pump, however, the outer size of the existing control valve is larger, and the regulation and control capability of the control valve is not ideal.
Disclosure of Invention
The invention aims to solve the technical problem of providing a constant pressure control valve of a high-flow high-pressure plunger pump, which has the advantages of compact volume, simple and convenient control, simple and convenient processing and manufacture and good pollution resistance, and can realize the remote control of the axial plunger pump.
The technical scheme adopted by the invention for solving the technical problems is as follows: the constant-pressure control valve of the high-flow high-pressure plunger pump comprises a valve body, a mounting seat, a valve core assembly, a limiting ejector rod assembly and a pressure regulating spring assembly, wherein the main body of the limiting ejector rod assembly is located in the mounting seat, the mounting seat is fixedly connected with the front end of the valve body, the front end of the limiting ejector rod assembly is fixedly connected with the rear end of the valve body, a first channel, a second channel, a third channel and an outward leakage channel are radially formed in the valve body from back to front, the first channel and the second channel are communicated with an outlet of the high-pressure plunger pump, the third channel is communicated with a large cavity of a variable oil cylinder, a valve core mounting cavity is formed in the valve body, the valve core assembly comprises a transition valve sleeve, a main slide valve core and an inner valve core, the transition valve sleeve is fixedly mounted in the valve core mounting cavity, and the outer side of the transition valve sleeve is sequentially provided with a first flow through hole corresponding to the first channel from back to front, A second flow through hole corresponding to the second channel, a third flow through hole corresponding to the third channel, and an external leakage oil return groove corresponding to the external leakage channel, wherein an inner annular groove communicated with the inner cavity of the transition valve sleeve is formed inside the first flow through hole, the main slide valve core can be arranged in the inner cavity of the transition valve sleeve in a back-and-forth movement manner, a first annular oil through groove and a second annular oil through groove are sequentially arranged at the side part of the main slide valve core from back to front, an annular sealing part is formed between the first annular oil through groove and the second annular oil through groove, the right end of the first annular oil through groove is sealed and separated from the third flow through hole through the annular sealing part, the second flow through hole is communicated with the first annular oil through groove, and the third flow through hole and the external leakage oil return groove are communicated with the second annular oil through groove, the rear end of the main sliding valve core is provided with a mounting hole, the inner valve core is accommodated in the mounting hole, an oil inlet hole communicated with the inner annular groove is formed in the hole wall of the mounting hole, a first oil guide groove and a second oil guide groove are formed in the rear end face of the main sliding valve core, the limiting ejector rod assembly is used for limiting outward sliding of the inner valve core, and the pressure regulating spring assembly is used for elastically abutting against the front end of the main sliding valve core backwards according to a preset elastic force value.
The limiting ejector rod component comprises a limiting seat, an ejector rod, a first adjusting screw rod, a first locking nut and a sealing nut, a first sealing element is arranged between the limiting seat and the valve body, a limiting cavity is arranged in the limiting seat, the ejector rod is movably arranged in the limiting cavity, the front end of the ejector rod is abutted to the rear end of the inner valve core, the rear end of the ejector rod is provided with a connecting screw hole, the front end of the first adjusting screw rod is screwed in the connecting screw hole, the rear end of the first adjusting screw rod extends backwards out of the limit cavity, the first locking nut and the sealing nut are sequentially screwed on the part of the first adjusting screw rod extending out of the limit seat from front to back, and a second sealing element is arranged between the first locking nut and the limiting seat, and a third sealing element is arranged between the sealing nut and the first locking nut. The ejector rod is used for limiting the inner valve core, the ejector rod utilizes the first adjusting screw rod to adjust the maximum axial opening amount and the sealing length of the main sliding valve core at the beginning, the first adjusting screw rod can push the ejector rod to move back and forth to adjust the sealing and opening distance of the main sliding valve core in the movement relative to the transition valve sleeve, the first adjusting screw rod is fixed by the first locking nut, and the first locking nut, the third sealing element and the fourth sealing element prevent pressure oil from leaking.
The pressure regulating spring assembly comprises an axial distance pressing sleeve, a first spring seat, a second spring seat, a spring, a second regulating screw, a regulating threaded sleeve, a second locking nut and an outer sealing head cap, wherein an installation part is axially and outwards protruded on the installation seat and is fixedly connected with the front end of the valve body through a screw, a fourth sealing element is arranged between the installation part and the valve body, the axial distance pressing sleeve is tightly pressed and arranged on the transition valve sleeve and between the installation seats, an internal thread is arranged on the inner side of the front end of the installation seat, an external thread matched with the internal thread is arranged on the outer side of the front end of the regulating threaded sleeve, the regulating threaded sleeve is screwed in the internal thread through the external thread, a fifth sealing element is arranged between the regulating threaded sleeve and the installation seat, and a screw hole is arranged in the regulating threaded sleeve, the rear end of the first spring seat is abutted to the front end of the main sliding valve core, the spring is arranged between the front end of the first spring seat and the rear end of the second spring seat in a compression mode, the front end of the second spring seat is abutted to the rear end of the second adjusting screw rod, the front end of the second adjusting screw rod is in threaded connection with the screw hole and stretches out forwards, the second locking nut and the outer head sealing cap are sequentially in threaded connection with the second adjusting screw rod from back to front and stretch out forwards of the screw hole, and a sixth sealing element is arranged between the adjusting threaded sleeve and the second adjusting screw rod. The preset elastic force value of the pressure regulating spring assembly can be selectively realized through the size of the spring.
The spring comprises a large spring and a small spring, the rear end of the first spring seat is in a spherical conical shape, the front end of the main sliding valve core is in a pincer-shaped structure, the rear end of the first spring seat is abutted to the front end of the main sliding valve core, a spring sleeve is arranged between the front end of the first spring seat and the rear end of the second spring seat, the large spring is sleeved on the spring sleeve in a compression mode, the first spring seat is located in the spring sleeve, a first mounting column is axially arranged at the center of the inner portion of the first spring seat, a second mounting column is axially arranged at the center of the inner portion of the second spring seat, and the small spring is sleeved on the first mounting column and the second mounting column in a compression mode. The pressure regulating spring assembly of the DN6 valve has the advantages of being simple and convenient to process and manage, convenient to assemble, disassemble and adjust, convenient to maintain and compact in size, the large spring and the small spring drive the second spring seat to move through the first adjusting screw rod to generate pre-thrust, the pressure of constant-pressure work of the high-pressure plunger pump is determined by the pre-thrust, and the thrust of the pressure regulating spring assembly can be increased by the design that the small spring is enlarged.
The rear end of the inner valve core is of an arc surface structure. The rear end of the inner valve core is of an arc surface structure, so that the stability of the main sliding valve core under thrust can be improved.
Compared with the prior art, the invention has the advantages that the pressure oil enters the valve core assembly through the first channel and the second channel on the valve body, the pressure oil entering from the first channel flows into the right end of the inner valve core through the first circulation hole, the inner annular groove and the oil inlet hole to push the inner valve core to slide outwards, in the movement process, the inner valve core is blocked by the mandril, so that the main sliding valve core is reversely pushed to move right to force the main sliding valve core to slide right, when the outward thrust of the inner valve core exceeds the set thrust of the pressure regulating spring assembly, the pressure oil entering from the second channel, pressure oil enters a third channel through a second circulation hole, a first oil guide groove and a second oil guide groove which are arranged on the rear end face of the main sliding valve core, a first annular oil guide groove and a third circulation hole, and pressure oil enters a large cavity of the variable oil cylinder from the third channel to push the variable oil cylinder to move to finish variable movement of the high-pressure plunger pump from large displacement to small displacement; when the pressure of the outlet of the high-pressure plunger pump is lower than the set pressure of the pressure-regulating spring assembly, the thrust of the spring in the pressure-regulating spring assembly overcomes the thrust of the inner valve core sliding outwards, pressure oil entering from the second channel enters the leakage channel through the second circulation hole, the first oil guide groove, the second oil guide groove and the leakage oil return groove which are arranged on the rear end face of the main sliding valve core, and the pressure oil leaks from the leakage channel to push the variable oil cylinder to move to finish the variable movement of the high-pressure plunger pump from small displacement to large displacement;
the inner valve core is arranged in the main sliding valve core, the inner valve core generates axial displacement to push the main sliding valve core under the action of pressure oil, and when the outlet pressure of the high-pressure plunger pump reaches the set pressure of the pressure regulating spring assembly, the displacement of the high-pressure plunger pump begins to be reduced; when the outlet pressure of the high-pressure plunger pump exceeds the set pressure of the pressure regulating spring assembly, the high-pressure plunger pump works at zero displacement; when the outlet pressure of the high-pressure plunger pump is reduced to be lower than the set pressure of the pressure regulating spring assembly, the high-pressure plunger pump is converted into large-displacement work;
pressure oil enters the valve core assembly from the first channel and the second channel, the main sliding valve core is pushed to enable the front end face of the main sliding valve core to move towards the pressure regulating spring assembly, the flow direction of the pressure oil can be controlled and changed, and therefore the variable oil cylinder is driven to carry out variable motion of the high-pressure plunger pump, when the flow area of the main sliding valve core is increased, namely the diameter of the main sliding valve core is increased, the sectional area of the inner valve core can be controlled to be reduced, the control thrust of the main sliding valve core under high pressure is reduced in a positive proportion, and therefore the thrust and the overall dimension of the pressure regulating spring assembly can be reduced;
the valve body is provided with a reserved control damping hole and an external control port, when the reserved control damping hole is opened and the inner valve core is removed, the two ends of the main sliding valve core have equal area to realize no pressure difference between the front end and the rear end, a small spring in the pressure regulating spring assembly can be removed, at the moment, oil enters from one side of the pressure regulating spring assembly through the reserved control damping hole, and meanwhile, the reserved external control port is connected with the constant pressure control valve to set the control pressure of the high-pressure plunger pump, so that the constant pressure control valve can be changed into a remote adjustable constant pressure valve;
the diameter of the main sliding valve core in the valve body is increased by increasing the diameter of the valve body, so that the response speed of the high-pressure plunger pump is increased, the inner valve core is arranged in the main sliding valve core, the axial thrust of the main sliding valve core under a high-pressure working condition can be reduced, and the control force of the pressure regulating spring assembly is reduced; when the diameter of the main sliding valve core is increased, the sectional area of the inner valve core is reduced, the thrust for pushing the main sliding valve core is kept unchanged, the adjusting force of the spring is small, and the appearance of the pressure regulating spring assembly is compact; when the set pressure needs to be remotely controlled and adjusted, the remote pressure control of the pressure oil introduced into the pressure regulating spring assembly can be realized only by disassembling the inner valve core in the valve core assembly.
Drawings
FIG. 1 is a cross-sectional view of the overall structure of the present invention when the high pressure plunger pump is at a high flow rate;
FIG. 2 is a cross-sectional view showing the overall structure of the high-pressure plunger pump according to the present invention when the high-pressure plunger pump has a small flow rate;
FIG. 3 is a cross-sectional view of the valve cartridge assembly of the present invention;
FIG. 4 is a cross-sectional view of a stop assembly of the present invention;
fig. 5 is a sectional view of a pressure regulating spring assembly according to the present invention.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
As shown in the figure, the constant pressure control valve of the high-flow high-pressure plunger pump comprises a valve body 1, a mounting seat 2, a valve core assembly, a limiting ejector rod assembly and a pressure regulating spring assembly, wherein a main body of the pressure regulating spring assembly is positioned in the mounting seat 2, the mounting seat 2 is fixedly connected with the front end of the valve body 1, the front end of the limiting ejector rod assembly is fixedly connected with the rear end of the valve body 1, a first channel 11, a second channel 12, a third channel 13 and an outward leakage channel 14 are radially formed in the valve body 1 from back to front, the first channel 11 and the second channel 12 are communicated with an outlet of the high-pressure plunger pump, the third channel 13 is communicated with a large cavity of a variable cylinder, a valve core mounting cavity 15 is formed in the valve body 1, the valve core assembly comprises a transition valve sleeve 3, a main slide valve core 4 and an inner valve core 5, the transition valve sleeve 3 is fixedly mounted in the valve core mounting cavity 15, and a first flow through hole 31, which corresponds to the first channel 11, is sequentially formed in the outer side of the transition valve sleeve 3 from back to front, A second flow through hole 32 corresponding to the second channel 12, a third flow through hole 33 corresponding to the third channel 13, and an external leakage oil groove 34 corresponding to the external leakage channel 14, wherein an inner annular groove 312 communicated with the inner cavity of the transition valve sleeve 3 is formed inside the first flow through hole 31, the main spool 4 is movably arranged in the inner cavity of the transition valve sleeve 3 in a back-and-forth manner, a first annular oil through groove 41 and a second annular oil through groove 42 are sequentially arranged from back to front on the side portion of the main spool 4, an annular sealing portion 43 is formed between the first annular oil through groove 41 and the second annular oil through groove 42, the right end of the first annular oil through groove 41 is sealed and separated from the third flow through hole 33 through the annular sealing portion 43, the second flow through hole 32 is communicated with the first annular oil through groove 41, the third flow through hole 33 and the external leakage oil groove 34 are communicated with the second annular oil through groove 42, a mounting hole 44 is formed at the rear end of the main spool 4, the inner valve core 5 is accommodated in the mounting hole 44, an oil inlet hole 441 communicated with the inner annular groove 312 is formed in the hole wall of the mounting hole 44, a first oil guide groove (not shown) and a second oil guide groove (not shown) are formed in the rear end face of the main sliding valve core 4, the limiting ejector rod assembly is used for limiting outward sliding of the inner valve core 5, and the pressure regulating spring assembly is used for elastically abutting against the front end of the main sliding valve core 4 backwards according to a preset elastic force value.
The limiting ejector rod assembly comprises a limiting seat 61, an ejector rod 62, a first adjusting screw rod 63, a first locking nut 64 and a sealing nut 65, a first sealing element 66 is arranged between the limiting seat 61 and the valve body 1, a limiting cavity 611 is arranged in the limiting seat 61, the ejector rod 62 is movably arranged in the limiting cavity 611, the front end of the ejector rod 62 is abutted to the rear end of the inner valve core 5, a connecting screw hole 621 is arranged at the rear end of the ejector rod 62, the front end of the first adjusting screw rod 63 is screwed in the connecting screw hole 621, the rear end of the first adjusting screw rod 63 extends out of the limiting cavity 611 backwards, the first locking nut 64 and the sealing nut 65 are sequentially screwed on the part of the first adjusting screw rod 63 extending out of the limiting seat 61 from front to back, a second sealing element 67 is arranged between the first locking nut 64 and the limiting seat 61, and a third sealing element 68 is arranged between the sealing nut 65 and the first locking nut 64.
The pressure regulating spring assembly comprises an axial distance pressing sleeve 71, a first spring seat 72, a second spring seat 73, a spring, a second regulating screw 74, a regulating threaded sleeve 75, a second locking nut 76 and an outer head cap 77, the mounting seat 2 is provided with a mounting part 21 which protrudes outwards in the axial direction, the mounting part 21 is fixedly connected with the front end of the valve body 1 through a screw (not shown), a fourth sealing element 78 is arranged between the mounting part 21 and the valve body 1, the axial distance pressing sleeve 71 is tightly pressed between the transition valve sleeve 3 and the mounting seat 2, the inner side of the front end of the mounting seat 2 is provided with an internal thread, the outer side of the front end of the regulating threaded sleeve 75 is provided with an external thread which is matched and screwed with the internal thread, the regulating threaded sleeve 75 is screwed in the internal thread through the external thread, a fifth sealing element 79 is arranged between the regulating threaded sleeve 75 and the mounting seat 2, a screw hole is arranged in the regulating threaded sleeve 75, the rear end of the first spring seat 72 is abutted to the front end of the main sliding valve core 4, the spring compression is arranged between the front end of the first spring seat 72 and the rear end of the second spring seat 73, the front end of the second spring seat 73 is abutted against the rear end of the second adjusting screw 74, the front end of the second adjusting screw 74 is screwed into the screw hole and extends forwards, the second lock nut 76 and the outer head cap 77 are screwed onto the part of the second adjusting screw 74 extending forwards in sequence from back to front, and a sixth sealing member 751 is arranged between the adjusting screw sleeve 75 and the second adjusting screw 74.
The spring comprises a large spring 81 and a small spring 82, the rear end of the first spring seat 72 is in a spherical conical shape, the front end of the main spool 4 is in a pincer-shaped structure, the rear end of the first spring seat 72 is connected with the front end of the main spool 4 in a butting mode, a spring sleeve 83 is arranged between the front end of the first spring seat 72 and the rear end of the second spring seat 73, the large spring 81 is sleeved on the spring sleeve 83 in a compression mode, a first mounting column 721 is axially arranged at the center of the inner portion of the spring sleeve 83 in the first spring seat 72, a second mounting column 731 is axially arranged at the center of the inner portion of the spring sleeve 83 in the second spring seat 73, and the small spring 82 is sleeved on the first mounting column 721 and the second mounting column 731 in a compression mode.
The rear end of the inner valve core 5 is of a circular arc surface structure.
The working principle of the above embodiment is as follows: the pressure oil enters into the valve core assembly through the first channel 11 and the second channel 12 on the valve body 1, the pressure oil entering from the first channel 11 flows into the right end of the inner valve core 5 through the first flow through hole 31, the inner annular groove 312 and the oil inlet hole 441, pushes the inner valve core 5 to slide outwards, in the movement process, the inner valve core 5 is blocked by the mandril 62, so that the main slide valve core 4 is reversely pushed to move right, the main slide valve core 4 is forced to slide right, when the outward thrust of the inner spool 5 exceeds the set thrust of the pressure regulating spring assembly, the pressure oil entering from the second passage 12, pressure oil enters the third channel 13 through the second through hole 32, a first oil guide groove (not shown) and a second oil guide groove (not shown) arranged on the rear end face of the main slide valve core 4, the first annular oil through groove 41 and the third through hole 33, and pressure oil enters a large cavity of the variable oil cylinder from the third channel 13 to push the variable oil cylinder to move so as to finish variable movement of the high-pressure plunger pump from large displacement to small displacement; when the pressure of the outlet of the high-pressure plunger pump is lower than the set pressure of the pressure-regulating spring assembly, the thrust of the spring in the pressure-regulating spring assembly overcomes the outward sliding thrust of the inner valve core 5, the pressure oil entering from the second channel 12 enters the leakage channel 14 through the second flow through hole 32, a first oil guide groove (not shown) and a second oil guide groove (not shown) arranged on the rear end surface of the main slide valve core 4 and an leakage oil return groove 34, the pressure oil is leaked from the leakage channel 14, and the variable oil cylinder is pushed to move to finish variable movement of the high-pressure plunger pump from small displacement to large displacement;
the inner valve core 5 is arranged in the main sliding valve core 4, the inner valve core 5 generates axial displacement to push the main sliding valve core 4 under the action of pressure oil, and when the outlet pressure of the high-pressure plunger pump reaches the set pressure of the pressure regulating spring assembly, the displacement of the high-pressure plunger pump begins to be reduced; when the outlet pressure of the high-pressure plunger pump exceeds the set pressure of the pressure regulating spring assembly, the high-pressure plunger pump works at zero displacement; when the outlet pressure of the high-pressure plunger pump is reduced to be lower than the set pressure of the pressure regulating spring assembly, the high-pressure plunger pump is converted into large-displacement work;
pressure oil enters the valve core assembly from the first channel 11 and the second channel 12, the main spool 4 is pushed to enable the front end face of the main spool 4 to move along the axial pre-compression large spring 81 and the small spring 82, the flow direction of the pressure oil can be controlled and changed, and therefore the variable cylinder is driven to carry out variable motion of the high-pressure plunger pump, when the flow area of the main spool 4 is increased, namely the diameter of the main spool 4 is increased, the sectional area of the inner spool 5 can be controlled to be reduced, the control thrust of the main spool 4 under high pressure is reduced in a positive proportion, and therefore the thrust and the overall dimension of the large spring 81 and the small spring 82 can be reduced;
the valve body 1 is provided with a reserved control damping hole and an external control port, when the reserved control damping hole is opened and the inner valve core 5 is removed, the two ends of the main sliding valve core 4 have equal area to realize no pressure difference between the front end and the rear end, the small spring 82 in the pressure regulating spring assembly can be removed, oil is fed into one side of the pressure regulating spring assembly through the reserved control damping hole, and meanwhile, the reserved external control port is connected with the constant pressure control valve to set the control pressure of the high-pressure plunger pump, so that the constant pressure control valve can be changed into a remote adjustable constant pressure control valve.
Claims (5)
1. The constant-pressure control valve of the high-flow high-pressure plunger pump is characterized by comprising a valve body, a mounting seat, a valve core assembly, a limiting ejector rod assembly and a pressure regulating spring assembly, wherein the valve body, the mounting seat, the front end of the valve body, the front end of the limiting ejector rod assembly and the main body are located in the mounting seat, the mounting seat is fixedly connected with the front end of the valve body, the front end of the limiting ejector rod assembly is fixedly connected with the rear end of the valve body, a first channel, a second channel, a third channel and an outward leakage channel are radially formed in the valve body from back to front, the first channel and the second channel are communicated with an outlet of the high-pressure plunger pump, the third channel is communicated with a large cavity of a variable oil cylinder, a valve core mounting cavity is formed in the valve body, the valve core assembly comprises a transition valve sleeve, a main sliding valve core and an inner valve core, the transition valve sleeve is fixedly mounted in the valve core mounting cavity, and the outer side of the transition valve sleeve is sequentially provided with a first flow through hole corresponding to the first channel from back to front, A second flow through hole corresponding to the second channel, a third flow through hole corresponding to the third channel, and an external leakage oil return groove corresponding to the external leakage channel, wherein an inner annular groove communicated with the inner cavity of the transition valve sleeve is formed inside the first flow through hole, the main slide valve core can be arranged in the inner cavity of the transition valve sleeve in a back-and-forth movement manner, a first annular oil through groove and a second annular oil through groove are sequentially arranged at the side part of the main slide valve core from back to front, an annular sealing part is formed between the first annular oil through groove and the second annular oil through groove, the right end of the first annular oil through groove is sealed and separated from the third flow through hole through the annular sealing part, the second flow through hole is communicated with the first annular oil through groove, and the third flow through hole and the external leakage oil return groove are communicated with the second annular oil through groove, the rear end of the main sliding valve core is provided with a mounting hole, the inner valve core is accommodated in the mounting hole, an oil inlet hole communicated with the inner annular groove is formed in the hole wall of the mounting hole, a first oil guide groove and a second oil guide groove are formed in the rear end face of the main sliding valve core, the limiting ejector rod assembly is used for limiting outward sliding of the inner valve core, and the pressure regulating spring assembly is used for elastically abutting against the front end of the main sliding valve core backwards according to a preset elastic force value.
2. The constant pressure control valve of the high-flow high-pressure plunger pump according to claim 1, characterized in that the limiting ejector rod assembly comprises a limiting seat, an ejector rod, a first adjusting screw rod, a first locking nut and a sealing nut, a first sealing element is arranged between the limiting seat and the valve body, a limiting cavity is arranged in the limiting seat, the ejector rod is movably arranged in the limiting cavity, the front end of the ejector rod is abutted to the rear end of the inner valve core, the rear end of the ejector rod is provided with a connecting screw hole, the front end of the first adjusting screw rod is screwed in the connecting screw hole, the rear end of the first adjusting screw rod extends backwards out of the limiting cavity, the first locking nut and the sealing nut are screwed in turn from front to back on the part of the first adjusting screw rod extending out of the limiting seat, and a second sealing element is arranged between the first locking nut and the limiting seat, and a third sealing element is arranged between the sealing nut and the first locking nut.
3. The constant pressure control valve of a large-flow high-pressure plunger pump according to claim 1, characterized in that the pressure regulating spring assembly comprises an axial distance pressing sleeve, a first spring seat, a second spring seat, a spring, a second adjusting screw, an adjusting screw sleeve, a second locking nut and an outer seal head cap, the mounting seat axially and outwards protrudes to form an installation part, the installation part is fixedly connected with the front end of the valve body through a screw, a fourth sealing element is arranged between the installation part and the valve body, the axial distance pressing sleeve is tightly pressed and arranged between the transition valve sleeve and the mounting seat, an internal thread is arranged on the inner side of the front end of the mounting seat, an external thread matched with the internal thread is arranged on the outer side of the front end of the adjusting screw sleeve, the adjusting screw sleeve is screwed in the internal thread through the external thread, the adjusting screw sleeve is provided with a fifth sealing element between the adjusting screw sleeve and the mounting seat, a screw hole is formed in the adjusting screw sleeve, the rear end of the first spring seat is abutted to the front end of the main sliding valve core, the spring is arranged between the front end of the first spring seat and the rear end of the second spring seat in a compression mode, the front end of the second spring seat is abutted to the rear end of the second adjusting screw rod, the front end of the second adjusting screw rod is screwed in the screw hole and extends forwards, the second locking nut and the outer seal head cap are sequentially screwed on the portion, extending forwards out of the screw hole, of the second adjusting screw rod from back to front, and a sixth sealing element is arranged between the adjusting screw sleeve and the second adjusting screw rod.
4. A constant pressure control valve of a high flow rate high pressure plunger pump according to claim 3, characterized in that said spring comprises a large spring and a small spring, the rear end of the first spring seat is spherical conical, the front end of the main slide valve core is of a pincer-shaped structure, the rear end of the first spring seat is abutted against the front end of the main slide valve core, a spring sleeve is arranged between the front end of the first spring seat and the rear end of the second spring seat, the large spring is sleeved on the spring sleeve in a compression manner, the first spring seat is positioned in the spring sleeve, the center of the inner part of the spring sleeve is axially provided with a first mounting column, a second mounting column is axially arranged at the center of the inner part of the spring sleeve of the second spring seat, the small spring is sleeved on the first mounting column and the second mounting column in a compression manner.
5. The constant pressure control valve of the high flow rate and high pressure plunger pump according to claim 1, characterized in that the rear end of the inner valve core is of a circular arc surface structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110712911.7A CN113530906A (en) | 2021-06-25 | 2021-06-25 | Constant pressure control valve of high-flow high-pressure plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110712911.7A CN113530906A (en) | 2021-06-25 | 2021-06-25 | Constant pressure control valve of high-flow high-pressure plunger pump |
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| CN113530906A true CN113530906A (en) | 2021-10-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110712911.7A Pending CN113530906A (en) | 2021-06-25 | 2021-06-25 | Constant pressure control valve of high-flow high-pressure plunger pump |
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| CN (1) | CN113530906A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1467603A (en) * | 1974-08-26 | 1977-03-16 | Koehring Co | Control valve for controlling the operation of a mechanism to be powered from a pressurised fluid supply |
| CN104234992A (en) * | 2013-11-20 | 2014-12-24 | 江苏恒立液压有限公司 | Plunger pump power control device and control method thereof |
| CN204327618U (en) * | 2014-05-15 | 2015-05-13 | 安徽博一流体传动股份有限公司 | pressure shut-off valve block assembly |
| CN204610163U (en) * | 2015-04-23 | 2015-09-02 | 宁波恒力液压股份有限公司 | Double steering constant-pressure variable axial piston pump |
| CN212838299U (en) * | 2020-07-03 | 2021-03-30 | 江苏津润智能科技有限公司 | Novel power valve for axial plunger pump |
-
2021
- 2021-06-25 CN CN202110712911.7A patent/CN113530906A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1467603A (en) * | 1974-08-26 | 1977-03-16 | Koehring Co | Control valve for controlling the operation of a mechanism to be powered from a pressurised fluid supply |
| CN104234992A (en) * | 2013-11-20 | 2014-12-24 | 江苏恒立液压有限公司 | Plunger pump power control device and control method thereof |
| CN204327618U (en) * | 2014-05-15 | 2015-05-13 | 安徽博一流体传动股份有限公司 | pressure shut-off valve block assembly |
| CN204610163U (en) * | 2015-04-23 | 2015-09-02 | 宁波恒力液压股份有限公司 | Double steering constant-pressure variable axial piston pump |
| CN212838299U (en) * | 2020-07-03 | 2021-03-30 | 江苏津润智能科技有限公司 | Novel power valve for axial plunger pump |
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| Title |
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| 林宁, 史津生: "KLINE恒压变量柱塞泵介绍", 液压与气动, no. 04, 15 August 1981 (1981-08-15), pages 53 - 55 * |
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