CN109268253B - Reciprocating pump with variable pressure increasing ratio - Google Patents
Reciprocating pump with variable pressure increasing ratio Download PDFInfo
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- CN109268253B CN109268253B CN201811461039.8A CN201811461039A CN109268253B CN 109268253 B CN109268253 B CN 109268253B CN 201811461039 A CN201811461039 A CN 201811461039A CN 109268253 B CN109268253 B CN 109268253B
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- 239000011148 porous material Substances 0.000 claims abstract description 14
- 230000006835 compression Effects 0.000 claims description 15
- 238000007906 compression Methods 0.000 claims description 15
- 239000003921 oil Substances 0.000 description 315
- 229910003460 diamond Inorganic materials 0.000 description 4
- 239000010432 diamond Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000003786 synthesis reaction Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000005034 decoration Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
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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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a variable-pressure-ratio reciprocating pump, which comprises a reversing valve, a left control valve, a right control valve, a pump shell with an axial pore channel, a left cylinder body with a left large plunger cavity and a left small plunger cavity, and a right cylinder body with a right large plunger cavity and a right small plunger cavity; the left cylinder body and the right cylinder body are respectively connected to the left end and the right end of an axial pore passage of the pump shell; a piston is connected in the axial pore channel of the pump shell in a sliding manner; the left end of the piston is provided with a left large plunger body and a left small plunger body; a left piston cavity is formed between the left end of the piston and the left cylinder body in an axial pore passage of the pump shell, and a right piston cavity is formed between the right end of the piston and the right cylinder body; the reciprocating pump not only has compact volume, but also has low cost and variable pressure ratio.
Description
Technical Field
The invention relates to the technical field of booster pumps, in particular to a reciprocating pump with variable booster ratio.
Background
The reciprocating booster pump is an important hydraulic element widely applied to a diamond cubic press, the outlet pressure is gradually boosted to about 100MPa through the reciprocating booster pump, the process requirement of diamond synthesis is met, the boosting speed is required to be the fastest in the diamond synthesis process under 60MPa, the boosting flow requirement is high at the moment, and the pressure maintaining stage is mainly above 60MPa, and the boosting flow requirement is low. In order to meet the requirements of diamond synthesis process, a large booster and a small booster are generally configured in the use of the conventional cubic press, the boosting ratio of the large booster is smaller, and the boosting ratio of the small booster can output large pressure but small output flow. The configuration of a large supercharger and a small supercharger is adopted, the complexity of the hydraulic oil circuit is increased, and the use cost is high.
Disclosure of Invention
Technical problem to be solved
The invention aims to overcome the defects in the prior art and provides a reciprocating pump with compact volume, low cost and variable pressure ratio.
(II) technical scheme
In order to achieve the purpose, the invention provides the following technical scheme: a reciprocating pump with variable pressurization ratio comprises a two-position four-way reversing valve, a two-position three-way left control valve, a two-position three-way right control valve, a pump shell with an axial pore channel, a left cylinder body with a left large plunger cavity and a left small plunger cavity, and a right cylinder body with a right large plunger cavity and a right small plunger cavity; the left cylinder body and the right cylinder body are respectively connected to the left end and the right end of an axial pore passage of the pump shell; a piston is connected in the axial pore channel of the pump shell in a sliding manner; the left end of the piston is provided with a left large plunger body which is connected in a sliding manner in the left large plunger cavity and a left small plunger body which is connected in a sliding manner in the left small plunger cavity; the right end of the piston is provided with a right large plunger body which is connected with the right large plunger cavity in a sliding mode, and a right small plunger body which is connected with the right small plunger cavity in a sliding mode, a left piston cavity is formed between the left end of the piston and the left cylinder body in an axial pore channel of the pump shell, and a right piston cavity is formed between the right end of the piston and the right cylinder body.
The P1 oil port of the reversing valve is communicated with the P oil port of the reciprocating pump, the T1 oil port is communicated with the T oil port of the reciprocating pump, the A1 oil port is communicated with the left piston cavity, and the B1 oil port is communicated with the right piston cavity.
A left one-way valve, a left two-way valve and a left three-way valve are arranged in the left cylinder body, an oil inlet of the left one-way valve is communicated with the left small plunger cavity, and an oil outlet of the left one-way valve is communicated with a high-pressure oil outlet of the reciprocating pump; the oil inlet of the left two one-way valve is communicated with the left big plunger cavity, and the oil outlet of the left two one-way valve is communicated with the high-pressure oil outlet of the reciprocating pump; and the oil inlet of the left three one-way valve is communicated with the oil port P of the reciprocating pump, and the oil outlet of the left three one-way valve is communicated with the left small plunger cavity.
The oil port D of the left control valve is communicated with the oil port P of the reciprocating pump, the oil port E of the left control valve is communicated with the oil port A1 of the reversing valve, the oil port C of the left control valve is communicated with the left large plunger cavity, and the control oil port of the left control valve is communicated with the high-pressure oil outlet of the reciprocating pump; when the pressure of the control oil port of the left control valve does not reach the switching pressure, the left control valve works at the right position, the oil port C of the left control valve is communicated with the oil port D, oil can only flow to the oil port C from the oil port D, when the pressure of the control oil port of the left control valve reaches the switching pressure, the left control valve is switched from the right position to the left position, and the oil port C is communicated with the oil port E.
A right one-way valve, a right two-way valve and a right three-way valve are arranged in the right cylinder body, an oil inlet of the right one-way valve is communicated with the right small plunger cavity, and an oil outlet of the right one-way valve is communicated with a high-pressure oil outlet of the reciprocating pump; an oil inlet of the right two one-way valves is communicated with the right big plunger cavity, and an oil outlet of the right two one-way valves is communicated with a high-pressure oil outlet of the reciprocating pump; and the oil inlet of the right three one-way valves is communicated with the oil port P of the reciprocating pump, and the oil outlet of the right three one-way valves is communicated with the right small plunger cavity.
The oil port D of the right control valve is communicated with the oil port P of the reciprocating pump, the oil port E of the right control valve is communicated with the oil port B1 of the reversing valve, the oil port C of the right control valve is communicated with the right large plunger cavity, and the control oil port is communicated with the high-pressure oil outlet of the reciprocating pump; when the pressure of the control oil port of the right control valve does not reach the switching pressure, the right control valve works at the right position, the oil port C of the right control valve is communicated with the oil port D, oil can only flow to the oil port C from the oil port D, when the right control valve is at the right position, when the pressure of the control oil port of the right control valve reaches the switching pressure, the right control valve is switched from the right position to the left position, and the oil port C is communicated with the oil port E.
Through the technical scheme, the left and right reciprocating motion of the piston is controlled by the reversing valve, when the reversing valve is in the right position, the P1 oil port is communicated with the B1 oil port, the T1 oil port is communicated with the A1 oil port, when the pressure of the high-pressure oil outlet of the reciprocating pump does not reach the switching pressure, the left control valve and the right control valve are both in the right position, the pressure oil enters the P oil port of the reciprocating pump, passes through the P1 oil port and the B1 oil port of the reversing valve, enters the right piston cavity to push the piston to move left, passes through the D oil port and the C oil port of the right control valve, enters the right small plunger cavity, passes through the right three one-way valves, enters the right small plunger cavity, and respectively pressurizes the pressure oil in the left small plunger cavity and the left large plunger cavity through the left small plunger body and the left large plunger body when the piston moves left, and is discharged to the high-pressure oil outlet of the reciprocating pump through the left one-way valve and the left two-way valve, and simultaneously, the oil in the left piston cavity is discharged to a T oil port of the reciprocating pump through an A1 oil port and a T1 oil port of the reversing valve; the large left plunger body and the small left plunger body of the reciprocating pump participate in pressurization, the pressurization ratio is small, and the output flow is large.
When the left end of the piston moves to the right end of the left cylinder body, the reversing valve works in the left position, the P1 oil port is communicated with the A1 oil port, the T1 oil port is communicated with the B1 oil port, when the pressure of the high-pressure oil outlet of the reciprocating pump does not reach the switching pressure, the left control valve and the right control valve are both in the right position, the pressure oil enters the P oil port of the reciprocating pump, enters the left piston cavity through the P1 oil port and the A1 oil port of the reversing valve to push the piston to move rightwards, enters the left large plunger cavity through the D oil port and the C oil port of the left control valve, enters the left small plunger cavity through the left three one-way valves, and respectively pressurizes the pressure oil in the right small plunger cavity and the right large plunger cavity through the right small plunger body and the right large plunger body when the piston moves rightwards, and is discharged to a high-pressure oil outlet of the reciprocating pump through the right one-way valve and the right two one-way valves, and simultaneously, the oil in the right piston cavity is discharged to a T oil port of the reciprocating pump through a B1 oil port and a T1 oil port of the reversing valve; the large right plunger body and the small right plunger body of the reciprocating pump participate in pressurization, the pressurization ratio is small, and the output flow is large.
When the pressure of the high-pressure oil outlet of the reciprocating pump reaches the switching pressure and the reversing valve is in the right position, the P1 oil port is communicated with the B1 oil port, the T1 oil port is communicated with the A1 oil port, the pressure oil of the high-pressure oil outlet of the reciprocating pump acts on the left control valve and the right control valve through the control oil ports of the left control valve and the right control valve to be switched to the left position, the pressure oil enters the P oil port of the reciprocating pump, enters the right piston cavity through the P1 oil port and the B1 oil port of the reversing valve to push the piston to move leftwards, enters the right large plunger cavity through the P1 oil port and the B1 oil port of the reversing valve and the E oil port and the C oil port of the right control valve, enters the right small plunger cavity through the three one-way valves, the pressure oil in the left small plunger cavity is pressurized through the left small plunger body and is discharged to the high-pressure oil outlet of the reciprocating pump through the left one-way valve, meanwhile, the oil in the left piston cavity is discharged to the T1, the oil in the left large plunger cavity is discharged to the T oil port of the reciprocating pump through the C oil port and the E oil port of the left control valve and the A1 oil port and the T1 oil port of the reversing valve; at the moment, only the left small plunger body is used for supercharging, the supercharging ratio is high, high output pressure can be achieved, and output flow is small.
When the pressure of the high-pressure oil outlet of the reciprocating pump reaches the switching pressure and the reversing valve is in the left position, the P1 oil port is communicated with the A1 oil port, the T1 oil port is communicated with the B1 oil port, the pressure oil of the high-pressure oil outlet of the reciprocating pump acts on the left control valve and the right control valve through the control oil ports of the left control valve and the right control valve to be switched to the left position, the pressure oil enters the P oil port of the reciprocating pump, enters the left piston cavity through the P1 oil port and the A1 oil port of the reversing valve to push the piston to move rightwards, enters the left large plunger cavity through the P1 oil port and the A1 oil port of the reversing valve and the E oil port and the C oil port of the left control valve, enters the left small plunger cavity through the left three one-way valves, the pressure oil in the right small plunger cavity is pressurized through the right small plunger body, the pressure oil is discharged to the high-pressure oil outlet of the reciprocating pump through the right one-way valve, and simultaneously, the oil in the right piston cavity is discharged, the oil in the right large plunger cavity is discharged to the T oil port of the reciprocating pump through the C oil port and the E oil port of the right control valve and the B1 oil port and the T1 oil port of the reversing valve; at the moment, only the small right plunger body is used for supercharging, the supercharging ratio is high, high output pressure can be achieved, and output flow is small.
In a further technical scheme, the left control valve and the right control valve have the same structure and respectively comprise a cartridge valve body, a plug, a switching valve core, a one-way valve core, a first compression spring, a second compression spring and a pressure sensitive valve core, wherein a first valve hole, a second valve hole, a third valve hole and a fourth valve hole which are communicated with each other are sequentially arranged in the cartridge valve body from the upper end to the lower end along the length direction of the cartridge valve body; an oil port D communicated with the first valve hole, an oil port C communicated with the second valve hole and an oil port E communicated with the third valve hole are formed in the circumferential side face of the plug-in valve body from the upper end to the lower end; and a control oil port communicated with the fourth valve hole is formed at the lower end of the cartridge valve body.
The plug is arranged in the first valve hole, and a fifth valve hole and a through flow hole which are communicated with each other are sequentially arranged in the plug from the upper end to the lower end along the axial direction of the first valve hole; the upper end of the switching valve core is connected in the fifth valve hole in a sliding manner, and the lower end of the switching valve core is connected in the third valve hole in a sliding manner; a convex shoulder is arranged on the circumferential side surface of the switching valve core positioned in the second valve hole, and the convex shoulder is matched with the upper end opening of the third valve hole to control the on-off of the third valve hole and the second valve hole; the upper end of the fifth valve hole is provided with an adjusting screw rod, and the first compression spring is arranged in the fifth valve hole and positioned between the adjusting screw rod and the switching valve core and used for forcing the shoulder to be compressed at the opening at the upper end of the third valve hole;
a first annular cutting groove communicated with the oil port D is formed in the circumferential side surface of the plug, and a first oil hole used for communicating the first annular cutting groove with the through flow hole is formed in the plug; the one-way valve core is positioned in the second valve hole and sleeved on the switching valve core, and the one-way valve core is matched with the lower end opening of the through flow hole and used for controlling the on-off of the second valve hole and the through flow hole; the second compression spring is sleeved on the switching valve core and is positioned between the one-way valve core and the convex shoulder to force the one-way valve core to be compressed at the opening at the lower end of the through flow hole; a second annular cutting groove communicated with the oil port E is formed in the circumferential side surface, close to the lower end, of the switching valve core;
the pressure sensitive valve core is connected in the fourth valve hole in a sliding mode, the upper end of the pressure sensitive valve core is located in the third valve hole, and a bulge used for preventing the pressure sensitive valve core from being separated from the fourth valve hole is arranged on the pressure sensitive valve core; and a first channel for communicating the fifth valve hole and the third valve hole is arranged in the switching valve core.
Through the technical scheme, when the pressure of the control oil port does not reach the set pressure of the first compression spring, oil enters from the D oil port and can push the one-way valve core to directly flow into the C oil port, the oil cannot flow into the D oil port (reversely cut off) from the C oil port, and the oil cannot flow into the C oil port from the E oil port (because the acting force of the E oil port on the switching valve core is balanced); when the pressure of the control oil port reaches the set pressure of the first compression spring, the pressure of the control oil port acts on the pressure sensitive valve core, the pressure sensitive valve core is pushed to move upwards, the switching valve core moves upwards to enable the oil port C and the oil port E to be communicated, and meanwhile, the switching valve core compresses the one-way valve core at the lower end opening of the through flow hole to cut off the communication between the oil port D and the oil port C.
In a further technical scheme, a spring seat is arranged between the upper end of the first compression spring and the lower end of the adjusting screw rod in the fifth valve hole.
(III) advantageous effects
Compared with the prior art, the technical scheme of the invention has the following advantages: the reciprocating pump can realize variable pressure ratio under different working conditions, and has compact volume, low installed power and low use cost compared with the prior art.
Drawings
FIG. 1 is a schematic diagram of a variable pumping ratio reciprocating pump according to the present invention;
FIG. 2 is a schematic diagram of the construction of the left and right control valves of the present invention;
FIG. 3 is a schematic view of the cartridge valve body according to the present invention.
Detailed Description
Referring to fig. 1-3, a variable pressure ratio reciprocating pump includes a two-position four-way reversing valve 8, a two-position three-way left control valve 7b, a two-position three-way right control valve 7a, a pump housing 001 with an axial hole, a left cylinder 3b with a left large plunger cavity 3b1 and a left small plunger cavity 3b2, and a right cylinder 3a with a right large plunger cavity 3a1 and a right small plunger cavity 3a 2; the left cylinder body 3b and the right cylinder body 3a are respectively connected to the left end and the right end of an axial pore passage of the pump shell 001; a piston 6 is connected in an axial pore channel of the pump shell 001 in a sliding manner; the left end of the piston 6 is provided with a left large plunger body 5b which is connected in a sliding way in the left large plunger cavity 3b1 and a left small plunger body 5d which is connected in a sliding way in the left small plunger cavity 3b 2; the right end of the piston 6 is provided with a right large plunger body 5a which is connected in a sliding way in the right large plunger cavity 3a1 and a right small plunger body 5c which is connected in a sliding way in the right small plunger cavity 3a2, and a left piston cavity 4b is formed between the left end of the piston 6 and the left cylinder body 3b in an axial duct of the pump shell 001 and a right piston cavity 4a is formed between the right end of the piston 6 and the right cylinder body 3 a.
The P1 oil port of the reversing valve 8 is communicated with the P oil port of the reciprocating pump, the T1 oil port is communicated with the T oil port of the reciprocating pump, the A1 oil port is communicated with the left piston cavity 4B, and the B1 oil port is communicated with the right piston cavity 4 a.
A left one-way valve 2d, a left two-way valve 2b and a left three-way valve 1b are arranged in the left cylinder body 3b, an oil inlet of the left one-way valve 2d is communicated with a left small plunger cavity 3b2, and an oil outlet of the left one-way valve is communicated with a high-pressure oil outlet H of the reciprocating pump; an oil inlet of the left second one-way valve 2b is communicated with the left large plunger cavity 3b1, and an oil outlet thereof is communicated with a high-pressure oil outlet H of the reciprocating pump; the oil inlet of the left three-way check valve 1b is communicated with the oil port P of the reciprocating pump, and the oil outlet of the left three-way check valve is communicated with the left small plunger chamber 3b 2.
The oil port D of the left control valve 7b is communicated with the oil port P of the reciprocating pump, the oil port E is communicated with the oil port A1 of the reversing valve 8, the oil port C is communicated with the left large plunger cavity 3b1, and the control oil port F is communicated with the high-pressure oil outlet H of the reciprocating pump; when the pressure of the control port F of the left control valve 7b does not reach the switching pressure, the left control valve 7b works at the left position, the port C of the left control valve 7b is communicated with the port D, and oil can only flow to the port C from the port D, when the pressure of the control port F of the left control valve 7b reaches the switching pressure, the left control valve 7b is switched to the left position from the right position, and the port C is communicated with the port E.
A right one-way valve 2c, a right two-way valve 2a and a right three-way valve 1a are arranged in the right cylinder body 3a, the oil inlet of the right one-way valve 2c is communicated with a right small plunger cavity 3a2, and the oil outlet thereof is communicated with a high-pressure oil outlet H of the reciprocating pump; an oil inlet of the right two-way valve 2a is communicated with the right large plunger cavity 3a1, and an oil outlet thereof is communicated with a high-pressure oil outlet H of the reciprocating pump; an oil inlet of the right three-way check valve 1a is communicated with an oil port P of the reciprocating pump, and an oil outlet of the right three-way check valve is communicated with the right small plunger cavity 3a 2.
The oil port D of the right control valve 7a is communicated with the oil port P of the reciprocating pump, the oil port E is communicated with the oil port B1 of the reversing valve 8, the oil port C is communicated with the right large plunger cavity 3a1, and the control oil port F is communicated with the high-pressure oil outlet H of the reciprocating pump; when the pressure of the control port F of the right control valve 7a does not reach the switching pressure, the right control valve 7a works at the right position, the port C of the right control valve 7a is communicated with the port D and oil can only flow to the port C from the port D, when the pressure of the control port F of the right control valve 7a reaches the switching pressure, the right control valve 7a is switched to the left position from the right position, and the port C is communicated with the port E.
The left control valve 7b and the right control valve 7a have the same structure and respectively comprise a plug-in valve body 1, a plug 5, a switching valve core 3, a one-way valve core 4, a first compression spring 7, a second compression spring 6 and a pressure sensitive valve core 2, wherein the diameter of the pressure sensitive valve core 2 is smaller than that of the switching valve core 3; a first valve hole 101, a second valve hole 102, a third valve hole 103 and a fourth valve hole 104 which are communicated with each other are sequentially arranged in the cartridge valve body 1 from the upper end to the lower end along the length direction; a D oil port communicated with the first valve hole 101, a C oil port communicated with the second valve hole 102 and an E oil port communicated with the third valve hole 103 are formed in the circumferential side surface of the cartridge valve body 1 from the upper end to the lower end; and a control oil port F communicated with the fourth valve hole 104 is formed at the lower end of the plug-in valve body 1.
The plug 5 is arranged in the first valve hole 101, and a fifth valve hole 501 and a through flow hole 502 which are communicated with each other are sequentially arranged in the plug 5 from the upper end to the lower end along the axial direction of the first valve hole 101; the upper end of the switching valve core 3 is connected in the fifth valve hole 501 in a sliding manner, and the lower end of the switching valve core is connected in the third valve hole 103 in a sliding manner; a shoulder 301 is arranged on the circumferential side surface of the switching valve core 3 positioned in the second valve hole 102, and the shoulder 301 is matched with the upper end opening of the third valve hole 103 for controlling the on-off of the third valve hole 103 and the second valve hole 102; an adjusting screw 9 is mounted at the upper end of the fifth valve hole 501, and the first pressing spring 7 is arranged in the fifth valve hole 501 and between the adjusting screw 9 and the switching valve core 3, and is used for forcing the shoulder 301 to press the opening at the upper end of the third valve hole 103.
A first annular cutting groove 503 communicated with the oil port D is formed in the circumferential side surface of the plug 5, and a first oil hole 504 communicated with the first annular cutting groove 503 and the through flow hole 502 is formed in the plug 5; the one-way valve core 4 is positioned in the second valve hole 102 and sleeved on the switching valve core 3, and is matched with the lower end opening of the through hole 502 to control the on-off of the second valve hole 102 and the through hole 502; the second compression spring 6 is sleeved on the switching valve core 3 and is positioned between the check valve core 4 and the shoulder 301 for forcing the check valve core 4 to be compressed at the lower end opening of the through hole 502; a second annular cutting groove 302 communicated with the E oil port is formed on the circumferential side surface of the switching valve core 3 close to the lower end; the pressure sensitive valve core 2 is slidably connected in the fourth valve hole 104, the upper end of the pressure sensitive valve core 2 is positioned in the third valve hole 103, and a protrusion 201 for preventing the pressure sensitive valve core 2 from being separated from the fourth valve hole 104 is arranged; the switching spool 3 is provided therein with a first passage 31 for communicating the fifth valve hole 501 and the third valve hole 103. A spring seat 10 is provided in the fifth valve hole 501 between the upper end of the first pressure spring 7 and the lower end of the adjusting screw 9.
When the reciprocating pump works, a P oil port of the reciprocating pump is connected with a low-pressure hydraulic pump, a T oil port of the reciprocating pump is connected with an oil tank, the left and right reciprocating motion of a piston 6 is controlled by a reversing valve 8, the reversing valve can adopt an electromagnetic reversing valve or a hydraulic control reversing valve with position pressure feedback, when the reversing valve 8 is in the right position, the P1 oil port is communicated with a B1 oil port, a T1 oil port is communicated with an A1 oil port, and when the pressure of a high-pressure oil outlet H of the reciprocating pump does not reach the switching pressure of 60MPa, a left control valve 7B and a right control valve 7a are both in the right position, pressure oil enters the P oil port of the reciprocating pump through a P1 oil port and a B1 oil port of the reversing valve 8 to push the piston 6 to move leftwards, enters a right large plunger cavity 3a1 through a D oil port and a C oil port of the right control valve 7a and enters a small plunger cavity 3a 355639 a through a three one-way valve 1a and enters a small plunger cavity 3a 2B 26B through a three-way valve 1a, and a small plunger body The pressure oil in the piston chamber 4b is pressurized and discharged to a high-pressure oil outlet H of the reciprocating pump through a left one-way valve 2d and a left two-way valve 2b, and meanwhile, the oil in the piston chamber 4b is discharged to a T oil port of the reciprocating pump through an A1 oil port and a T1 oil port of a reversing valve 8; this makes both the large left plunger body 5b and the small left plunger body 5d of the reciprocating pump participate in the pressurization, the pressurization ratio is small, and the output flow rate is large.
When the left end of the piston 6 moves to the right end of the left cylinder body 3B, the reversing valve 8 works at the left position, the P1 oil port is communicated with the A1 oil port, the T1 oil port is communicated with the B1 oil port, and the pressure of the high-pressure oil outlet H of the reciprocating pump does not reach the switching pressure of 60Mpa, the left control valve 7B and the right control valve 7a are both at the right position, pressure oil enters the P oil port of the reciprocating pump through the P1 oil port and the A1 oil port of the reversing valve 8 to enter the left piston cavity 4B to push the piston 6 to move rightwards, enters the left large plunger cavity 3B1 through the D oil port and the C oil port of the left control valve 7B, enters the left small plunger cavity 3B2 through the left three-way valve 1B, the pressure oil in the right small plunger cavity 3a2 and the right large plunger cavity 3a1 is respectively pressurized through the right small plunger body 5C and the right large plunger body 5a when the piston 6 moves rightwards, and the high-pressure oil outlet of the right one-way check valve 2C and the high-pressure, meanwhile, the oil in the right piston chamber 4a is discharged to the T port of the reciprocating pump through the B1 port and the T1 port of the directional control valve 8; this causes both the large right plunger body 5a and the small right plunger body 5c of the reciprocating pump to participate in the pressurization, the pressurization ratio is small, and the output flow rate is large.
When the pressure of a high-pressure oil outlet H of the reciprocating pump reaches switching pressure 60Mpa and the reversing valve 8 is in a right position, a P1 oil port is communicated with a B1 oil port, a T1 oil port is communicated with an A1 oil port, pressure oil of the high-pressure oil outlet H of the reciprocating pump acts on the left control valve 7B and the right control valve 7a through control oil ports F of the left control valve 7B and the right control valve 7a to enable the pressure oil to be switched to the left position, the pressure oil enters the P oil port of the reciprocating pump, enters the right piston cavity 4a through the P1 oil port and the B1 oil port of the reversing valve 8 to push the piston 6 to move leftwards, enters the right large plunger cavity 3a1 through the P1 and the B1 oil ports of the reversing valve 8 and the E oil port and the C of the right control valve 7a, enters the small plunger cavity 3a2 through the three one-way valve 1a right, when the piston 6 moves leftwards, the pressure oil in the small plunger cavity 3B2 is pressurized through the small left plunger body 5d, and is discharged to the high-, meanwhile, the oil in the left piston cavity 4b is discharged to the T oil port of the reciprocating pump through the a1 oil port and the T1 oil port of the reversing valve 8, and the oil in the left large plunger cavity 3b1 is discharged to the T oil port of the reciprocating pump through the C oil port and the E oil port of the left control valve 7b and the a1 oil port and the T1 oil port of the reversing valve 8; at the moment, only the left small plunger body 5d is used for supercharging, the supercharging ratio is high, high output pressure can be achieved, and output flow is small.
When the pressure of a high-pressure oil outlet H of the reciprocating pump reaches switching pressure 60Mpa and the reversing valve 8 is in a left position, a P1 oil port is communicated with an A1 oil port, a T1 oil port is communicated with a B1 oil port, pressure oil of the high-pressure oil outlet H of the reciprocating pump acts on the left control valve 7B and the right control valve 7a through control oil ports F of the left control valve 7B and the right control valve 7a to enable the left position to be switched, the pressure oil enters the P oil port of the reciprocating pump, enters the left piston cavity 4B through the P1 oil port and the A1 oil port of the reversing valve 8 to push the piston 6 to move rightwards, enters the left large plunger cavity 3B1 through the P1 oil port and the A1 oil port of the reversing valve 8 and the E oil port and the C oil port of the left control valve 7B, enters the left small plunger cavity 3B2 through the left three one-way valve 1B, when the piston 6 moves rightwards, the pressure oil in the right small plunger cavity 3a2 is pressurized through the right small plunger body 5C, and is discharged to the high-pressure, meanwhile, the oil in the right piston cavity 4a is discharged to the T oil port of the reciprocating pump through the B1 oil port and the T1 oil port of the reversing valve 8, and the oil in the right large plunger cavity 3a1 is discharged to the T oil port of the reciprocating pump through the C oil port and the E oil port of the right control valve 7a and the B1 oil port and the T1 oil port of the reversing valve 8; at the moment, only the small right plunger body 5c is used for supercharging, the supercharging ratio is high, high output pressure can be achieved, and output flow is small.
In the working process of the left control valve 7b and the right control valve 7a, when the pressure of the control oil port F does not reach the set pressure of the first hold-down spring 7, the oil enters from the oil port D, passes through the first annular cutting groove 503, the first oil hole 504 and the through flow groove 502, can push the one-way valve core 4 open, and directly flows into the oil port C, but cannot flow into the oil port D (reverse cut-off) from the oil port C, and cannot flow into the oil port C from the oil port E (because the acting force of the oil port E on the switching valve core 3 is balanced); when the pressure of the control oil port F reaches the set pressure of the first hold-down spring 7, the pressure of the control oil port F acts on the pressure sensitive valve core 2, so that the pressure sensitive valve core pushes the switching valve core 3 to move upwards, the switching valve core 3 moves upwards to enable the oil port C and the oil port E to be communicated, and meanwhile, the switching valve core 3 compresses the one-way valve core 4 at the lower opening of the through-flow hole 502, so that the communication between the oil port D and the oil port C is cut off.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the technical principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.
Claims (3)
1. A reciprocating pump with a variable pressurization ratio is characterized by comprising a two-position four-way reversing valve, a two-position three-way left control valve, a two-position three-way right control valve, a pump shell with an axial pore channel, a left cylinder body with a left large plunger cavity and a left small plunger cavity, and a right cylinder body with a right large plunger cavity and a right small plunger cavity; the left cylinder body and the right cylinder body are respectively connected to the left end and the right end of an axial pore passage of the pump shell; a piston is connected in the axial pore channel of the pump shell in a sliding manner; the left end of the piston is provided with a left large plunger body which is connected in a sliding manner in the left large plunger cavity and a left small plunger body which is connected in a sliding manner in the left small plunger cavity; the right end of the piston is provided with a right large plunger body which is connected in a sliding manner in the right large plunger cavity and a right small plunger body which is connected in the right small plunger cavity in a sliding manner, a left piston cavity is formed between the left end of the piston and the left cylinder body in an axial pore passage of the pump shell, and a right piston cavity is formed between the right end of the piston and the right cylinder body;
a P1 oil port of the reversing valve is communicated with a P oil port of the reciprocating pump, a T1 oil port is communicated with a T oil port of the reciprocating pump, an A1 oil port is communicated with the left piston cavity, and a B1 oil port is communicated with the right piston cavity;
a left one-way valve, a left two-way valve and a left three-way valve are arranged in the left cylinder body, an oil inlet of the left one-way valve is communicated with the left small plunger cavity, and an oil outlet of the left one-way valve is communicated with a high-pressure oil outlet of the reciprocating pump; the oil inlet of the left two one-way valve is communicated with the left big plunger cavity, and the oil outlet of the left two one-way valve is communicated with the high-pressure oil outlet of the reciprocating pump; an oil inlet of the left three one-way valve is communicated with an oil port P of the reciprocating pump, and an oil outlet of the left three one-way valve is communicated with the left small plunger cavity;
the oil port D of the left control valve is communicated with the oil port P of the reciprocating pump, the oil port E of the left control valve is communicated with the oil port A1 of the reversing valve, the oil port C of the left control valve is communicated with the left large plunger cavity, and the control oil port of the left control valve is communicated with the high-pressure oil outlet of the reciprocating pump; when the pressure of the control oil port of the left control valve reaches the switching pressure, the left control valve works at the right position, the oil port C of the left control valve is communicated with the oil port D, oil can only flow to the oil port C from the oil port D, and when the pressure of the control oil port of the left control valve reaches the switching pressure, the left control valve is switched from the right position to the left position, and the oil port C is communicated with the oil port E;
a right one-way valve, a right two-way valve and a right three-way valve are arranged in the right cylinder body, an oil inlet of the right one-way valve is communicated with the right small plunger cavity, and an oil outlet of the right one-way valve is communicated with a high-pressure oil outlet of the reciprocating pump; an oil inlet of the right two one-way valves is communicated with the right big plunger cavity, and an oil outlet of the right two one-way valves is communicated with a high-pressure oil outlet of the reciprocating pump; an oil inlet of the right three one-way valve is communicated with an oil port P of the reciprocating pump, and an oil outlet of the right three one-way valve is communicated with the right small plunger cavity;
the oil port D of the right control valve is communicated with the oil port P of the reciprocating pump, the oil port E of the right control valve is communicated with the oil port B1 of the reversing valve, the oil port C of the right control valve is communicated with the right large plunger cavity, and the control oil port is communicated with the high-pressure oil outlet of the reciprocating pump; when the pressure of the control oil port of the right control valve does not reach the switching pressure, the right control valve works at the right position, the oil port C of the right control valve is communicated with the oil port D, oil can only flow to the oil port C from the oil port D, when the right control valve is at the right position, when the pressure of the control oil port of the right control valve reaches the switching pressure, the right control valve is switched from the right position to the left position, and the oil port C is communicated with the oil port E.
2. The reciprocating pump with the variable pressure ratio according to claim 1, wherein the left control valve and the right control valve have the same structure and comprise a cartridge valve body, a plug, a switching valve core, a one-way valve core, a first compression spring, a second compression spring and a pressure sensitive valve core, and a first valve hole, a second valve hole, a third valve hole and a fourth valve hole which are communicated with each other are sequentially arranged in the cartridge valve body from the upper end to the lower end along the length direction of the cartridge valve body; an oil port D communicated with the first valve hole, an oil port C communicated with the second valve hole and an oil port E communicated with the third valve hole are formed in the circumferential side face of the plug-in valve body from the upper end to the lower end; the lower end of the plug-in valve body is provided with a control oil port communicated with the fourth valve hole;
the plug is arranged in the first valve hole, and a fifth valve hole and a through flow hole which are communicated with each other are sequentially arranged in the plug from the upper end to the lower end along the axial direction of the first valve hole; the upper end of the switching valve core is connected in the fifth valve hole in a sliding manner, and the lower end of the switching valve core is connected in the third valve hole in a sliding manner; a convex shoulder is arranged on the circumferential side surface of the switching valve core positioned in the second valve hole, and the convex shoulder is matched with the upper end opening of the third valve hole to control the on-off of the third valve hole and the second valve hole; the upper end of the fifth valve hole is provided with an adjusting screw rod, and the first compression spring is arranged in the fifth valve hole and positioned between the adjusting screw rod and the switching valve core and used for forcing the shoulder to be compressed at the opening at the upper end of the third valve hole;
a first annular cutting groove communicated with the oil port D is formed in the circumferential side surface of the plug, and a first oil hole used for communicating the first annular cutting groove with the through flow hole is formed in the plug; the one-way valve core is positioned in the second valve hole and sleeved on the switching valve core, and the one-way valve core is matched with the lower end opening of the through flow hole and used for controlling the on-off of the second valve hole and the through flow hole; the second compression spring is sleeved on the switching valve core and is positioned between the one-way valve core and the convex shoulder to force the one-way valve core to be compressed at the opening at the lower end of the through flow hole; a second annular cutting groove communicated with the oil port E is formed in the circumferential side surface, close to the lower end, of the switching valve core;
the pressure sensitive valve core is connected in the fourth valve hole in a sliding mode, the upper end of the pressure sensitive valve core is located in the third valve hole, and a bulge used for preventing the pressure sensitive valve core from being separated from the fourth valve hole is arranged on the pressure sensitive valve core; and a first channel for communicating the fifth valve hole and the third valve hole is arranged in the switching valve core.
3. The variable boost ratio reciprocating pump of claim 2, wherein a spring seat is provided in the fifth valve hole between the upper end of the first compression spring and the lower end of the adjustment screw.
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| CN201811461039.8A CN109268253B (en) | 2018-12-01 | 2018-12-01 | Reciprocating pump with variable pressure increasing ratio |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111502945B (en) * | 2020-04-22 | 2023-01-06 | 湖南中崛水设备股份有限公司 | Booster water pump with variable booster ratio |
| CN111502944B (en) * | 2020-04-22 | 2023-05-30 | 东营盛昶石油机械有限公司 | Reciprocating high-pressure plunger pump |
| CN112128151B (en) * | 2020-09-15 | 2022-05-13 | 广东精克仕动力技术有限公司 | Automatic continuous circulation pressure cylinder |
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| CN2048910U (en) * | 1989-04-06 | 1989-12-06 | 徐学新 | Reversing valve |
| CN102705275A (en) * | 2012-06-25 | 2012-10-03 | 三一重工股份有限公司 | Hydraulic control system for bolt and engineering machinery |
| CN206112224U (en) * | 2016-10-12 | 2017-04-19 | 朱宝京 | There is not two -position three way of leakage electromagnetism cone valve |
| CN108679008A (en) * | 2018-07-19 | 2018-10-19 | 江苏师范大学 | A kind of continuous output booster and control method of changeable pressure ratio |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU954642A1 (en) * | 1980-06-12 | 1982-08-30 | Предприятие П/Я А-7393 | Pneumohydraulic booster |
| CN101463844A (en) * | 2008-12-23 | 2009-06-24 | 大连海事大学 | Gas-saving type gas supercharger using double activation pistons |
| CN108730145B (en) * | 2018-05-18 | 2020-06-02 | 高建国 | Hydraulic slurry pump |
| CN108425665B (en) * | 2018-05-18 | 2019-08-27 | 阿奥艾斯能源科技成都有限公司 | A kind of fracturing pump of hydraulic-driven |
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2018
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2048910U (en) * | 1989-04-06 | 1989-12-06 | 徐学新 | Reversing valve |
| CN102705275A (en) * | 2012-06-25 | 2012-10-03 | 三一重工股份有限公司 | Hydraulic control system for bolt and engineering machinery |
| CN206112224U (en) * | 2016-10-12 | 2017-04-19 | 朱宝京 | There is not two -position three way of leakage electromagnetism cone valve |
| CN108679008A (en) * | 2018-07-19 | 2018-10-19 | 江苏师范大学 | A kind of continuous output booster and control method of changeable pressure ratio |
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