CN108612682B - A kind of low noise hydraulic intensifier - Google Patents
A kind of low noise hydraulic intensifier Download PDFInfo
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- CN108612682B CN108612682B CN201810479398.XA CN201810479398A CN108612682B CN 108612682 B CN108612682 B CN 108612682B CN 201810479398 A CN201810479398 A CN 201810479398A CN 108612682 B CN108612682 B CN 108612682B
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- 238000000034 method Methods 0.000 description 5
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
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Classifications
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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
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/008—Reduction of noise or vibration
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- Braking Systems And Boosters (AREA)
Abstract
The invention discloses a kind of low noise hydraulic intensifiers comprising pressurizing pack, liquid controlled reversing valve module, buffer-braking component.The both ends plunger shaft of booster low-pressure piston is equipped with through-flow slot, when piston is mobile to side, when through-flow slot when the side is covered by piston, oil liquid can only be flowed out by the sequence valve in the side one way sequence valve, therefore brake pressure is generated to the low pressure chamber of the side by the one way sequence valve of the side, on the one hand make piston generate braking to stop, the end cap of the side will not be met, and then noise will not be generated, on the other hand the overflow valve being connected with other side low pressure chamber is triggered to open, to promote the spool of liquid controlled reversing valve module mobile, flow direction change, to which high pressure oil flows into the low pressure chamber of the side through the through-flow slot and one way sequence valve of the side, push piston mobile to the other side, repeatedly.The present invention can not only realize automatic continuous pressurization, and generate shock between end cap when avoiding piston motion, greatly reduce noise.
Description
Technical Field
The invention relates to the technical field of hydraulic superchargers, in particular to a low-noise hydraulic supercharger which can reliably and automatically supercharge continuously.
Background
The hydraulic pressure booster is an ultrahigh pressure hydraulic component which amplifies hydraulic pressure by utilizing the principle that the action areas of two ends of a piston are different and the stress sizes are the same, and the hydraulic pressure booster can increase low pressure to 200MPa or above. The hydraulic pressure booster can be divided into a single-acting single-stroke booster, a single-acting reciprocating booster and a double-acting reciprocating booster. The single-action single-stroke supercharger is limited by stroke because of the movement in one direction, the output flow is limited, the continuous supercharging can not be achieved, and the application range is narrow. The single-action reciprocating supercharger can realize continuous supercharging, but only can realize single-way supercharging, the utilization rate of an oil source is only half, and the output flow is limited. The double-acting reciprocating hydraulic pressure booster can realize bidirectional continuous boosting, is not limited by stroke, has large output flow and is an ideal boosting element. However, the traditional double-acting reciprocating hydraulic pressure booster adopted in China at present controls the reciprocating motion of a pressure boosting cylinder to continuously output high pressure through continuous reversing of an electromagnetic reversing valve, and the traditional double-acting reciprocating hydraulic pressure booster is complex in structure, large in size and weight, inconvenient to carry and difficult to adopt in the aspects of inflammable and explosive occasions and portable machinery.
Chinese patent application No. CN101666339 discloses a hydraulic pressure booster, and proposes a scheme for controlling continuous movement of a pressure cylinder by using a stroke control reversing valve and a main reversing valve, which has innovative points compared with the traditional domestic double-acting pressure booster using an electromagnetic reversing valve to control reversing, but also has the following disadvantages:
1. because the stroke reversing valve is kept at two positions by utilizing the positioning of the steel ball and the chain, the booster cylinder is controlled to move towards different directions, the structure is complex, and the processing difficulty is high. The positioning of the steel ball is easy to lose efficacy, and when the chain is broken, the stroke control reversing valve is located at a floating position, namely the pressure cylinder stops moving, so that the control mode is unreliable;
2. the stroke control valve and the main reversing valve are adopted for two-stage control, so that on one hand, the structure is more complex; on the other hand, the supercharging frequency of the supercharger is reduced, and the large flow output cannot be achieved.
3. When the piston moves to the head in one direction, the piston can collide with the end cover in the corresponding direction, and in the continuous high-frequency motion, the continuous collision between the piston and the end cover generates great noise and has adverse effect on the service life.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides the low-noise hydraulic pressure booster which not only can realize automatic continuous pressurization, but also avoids the collision between the piston and the end cover during the movement of the piston, thereby greatly reducing the noise.
In order to solve the problems in the prior art, the adopted specific technical scheme is as follows:
the utility model provides a low noise hydraulic pressure booster, its includes pressure boost subassembly, liquid accuse switching-over valve subassembly, the pressure boost subassembly includes low pressure piston, left high pressure piston, right high pressure piston, left side high pressure piston and right high pressure piston link to each other with the left and right both ends of low pressure piston respectively, and form left high pressure chamber and right high pressure chamber respectively on the left side of left high pressure piston and the right side of right high pressure piston, form left low pressure chamber and right low pressure chamber respectively on the left side of low pressure piston and right side, left side high pressure chamber and right high pressure chamber communicate with the high-pressure delivery outlet through first left check valve and first right check valve respectively.
The buffer brake assembly comprises a left one-way sequence valve, a right one-way sequence valve, a left overflow valve and a right overflow valve; the hydraulic control reversing valve assembly is characterized in that a plurality of protruding rings arranged at intervals are arranged on the two ends of a reversing valve core and the middle outer circumference of the reversing valve core in the hydraulic control reversing valve assembly, a left control cavity and a right control cavity are formed at the left end and the right end of the reversing valve core respectively, and an oil inlet, an oil return opening, a first oil port and a second oil port are formed in the hydraulic control reversing valve assembly.
The inner walls of two ends of the left low-pressure cavity and the right low-pressure cavity are respectively provided with a left through flow groove and a right through flow groove which are annular, and the diameters of the left through flow groove and the right through flow groove are both larger than that of the low-pressure piston; the left through flow groove communicates the left low-pressure cavity with the first oil port, and the right through flow groove connects the right low-pressure cavity with the second oil port; when the low-pressure piston moves to the right, the right through-flow groove is covered, and when the low-pressure piston moves to the left, the left through-flow groove is covered; the left check sequence valve and the right check sequence valve are connected to the left end and the right end of the left low-pressure cavity and the right low-pressure cavity respectively, the left check sequence valve connects the left low-pressure cavity with the first oil port, and the right check sequence valve connects the right low-pressure cavity with the second oil port.
An oil inlet of the left overflow valve is communicated with the first oil port, the left through flow groove and the left one-way sequence valve, and an oil return port of the left overflow valve is connected with a left control cavity of the hydraulic control reversing valve component, an oil inlet of the left hydraulic control one-way valve and a control oil port of the right hydraulic control one-way valve; an oil inlet of the right overflow valve is communicated with the second oil port, the right through flow groove and the right one-way sequence valve, and an oil return port of the right overflow valve is connected with a right control cavity of the hydraulic control reversing valve assembly, a control oil port of the left hydraulic control one-way valve and an oil inlet of the right hydraulic control one-way valve; the oil return ports of the left hydraulic control one-way valve and the right hydraulic control one-way valve are communicated with the oil return port of the hydraulic control reversing valve assembly; when the left overflow valve is in a opened state, the right hydraulic control one-way valve is opened, the reversing valve core moves rightwards, the oil inlet is communicated with the second oil port, and the first oil port is communicated with the oil return port; when the right overflow valve is opened, the left hydraulic control check valve is opened, the reversing valve core moves leftwards, the oil inlet is communicated with the first oil port, and the second oil port is communicated with the oil return port.
Preferably, in order to describe the arrangement structure of the raised ring on the reversing valve core more conveniently, a method described by functional limitation is adopted, and the arrangement of the raised ring on the reversing valve core meets the following requirements: when the reversing valve core moves leftwards, the oil inlet is communicated with the first oil port, and the second oil port is communicated with the oil return port; when the reversing valve core moves rightwards, the oil inlet is communicated with the second oil port, and the first oil port is communicated with the oil return port. Four protruding rings are sequentially arranged on the reversing valve core from left to right: first left bulge loop, second right bulge loop, a right bulge loop, the lower part of switching-over case is provided with five hydraulic fluid ports: the oil return device comprises a first oil return port, a first oil port, an oil inlet, a second oil port and a second oil return port which are sequentially arranged from left to right, wherein the first oil return port and the second oil return port are communicated to form the oil return port. When the reversing valve core moves leftwards, the oil inlet and the first oil port are communicated between the left two bulge rings and the right two bulge rings, and the second oil port and the second oil return port are communicated between the right two bulge rings and the right one bulge ring; when the reversing valve core moves rightwards, the first oil port and the first oil return port are communicated between the left first raised ring and the left second raised ring, and the oil inlet and the second oil port are communicated between the left second raised ring and the right second raised ring.
In a further preferred scheme, the left high-pressure cavity and the right high-pressure cavity are communicated with the oil inlet through a second left check valve and a second right check valve respectively.
In a further preferred scheme, the hydraulic control reversing valve assembly comprises a valve body, a control valve core arranged in a cavity of the valve body and end covers arranged at two ends of the control valve core; and the left overflow valve, the right overflow valve, the left hydraulic control one-way valve and the right hydraulic control one-way valve are all fixed on the valve body. The hydraulic control reversing valve component adopts the mechanism, so that the structure is simpler and the assembly is more convenient. And the left overflow valve, the right overflow valve, the left hydraulic control one-way valve and the right hydraulic control one-way valve are all fixed on the valve body, so that the whole device is smaller in size and more convenient to carry.
By adopting the scheme, compared with the prior art, the low-noise hydraulic supercharger has the technical effects that:
(1) the two sides of the left low-pressure cavity and the right low-pressure cavity are both connected with one-way sequence valves and provided with flow through grooves, when a low-pressure piston moves left and right to cover the left flow through groove or the right flow through groove, the one-way sequence valves generate braking pressure on the piston cavity, on one hand, the piston stops braking, the piston does not touch end covers at two ends, noise is not generated, on the other hand, an overflow valve can be triggered to open, a hydraulic control reversing valve assembly is reversed, the moving direction of the piston is changed, and therefore the pressurizing cylinder continuously outputs high pressure in a reciprocating mode and is noiseless.
(2) The left overflow valve, the right overflow valve, the left hydraulic control one-way valve and the right hydraulic control one-way valve are all arranged on the valve body of the hydraulic control reversing valve assembly, so that the whole structure is more compact, the size is smaller, the application range is wider, and the carrying is more convenient.
(3) Compared with the prior art, the high-frequency supercharging device has the advantages of simpler structure, more reliable operation and capability of achieving the purpose of high-frequency supercharging.
Drawings
FIG. 1 is a schematic diagram of a low noise hydraulic booster of the present invention;
FIG. 2 is a schematic illustration of the piston of a low noise hydraulic booster of the present invention moving to the right end position;
FIG. 3 is a schematic illustration of the piston of a low noise hydraulic booster of the present invention moving to the left end position;
FIG. 4 is a cross-sectional view of a hydraulic control directional control valve assembly of a low noise hydraulic booster of the present invention;
FIG. 5 is a sectional view taken along line A-A of FIG. 4;
fig. 6 is a cross-sectional view taken along line B-B in fig. 5.
The labels in the figures are: p, an oil inlet; t, an oil return port; t1, a first oil return port; t2, second oil return port; A. a first oil port; B. a second oil port; H. a high pressure output port; 1a, a second left check valve; 1b, a second right check valve; 2a, a first left check valve; 2b, a first right check valve; 3a, a left high-pressure cavity; 3b, a right high-pressure cavity; 4a, a left low-pressure cavity; 4b, a right low-pressure cavity; 5a, a left high-pressure piston; 5b, a right high-pressure piston; 6a, a left one-way sequence valve; 6b, a right one-way sequence valve; 7a, a left through flow groove; 7b, a right through flow groove; 8a, a left overflow valve; 8b, a right overflow valve; 9. a reversing valve core; 91. a left raised ring; 92. a left two-convex ring; 93. a right two-convex ring; 94. a right bulge loop; 10a, a left hydraulic control one-way valve; 10b, a right hydraulic control one-way valve; 11. a low pressure piston; 11a, a left control cavity; 11b, right control chamber.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to the accompanying drawings in combination with specific examples. It should be understood that the description is intended to be exemplary only, and is not intended to limit the scope of the present invention. Moreover, in the following description, descriptions of well-known structures and techniques are omitted so as to not unnecessarily obscure the concepts of the present invention.
The low noise hydraulic booster of the present invention, as shown in fig. 1 to 6, is a preferred embodiment.
The low-noise hydraulic pressure booster comprises a pressure boosting assembly, a hydraulic control reversing valve assembly and a buffering brake assembly. The pressure boost subassembly includes low pressure piston 11, left high pressure piston 5a, right high pressure piston 5b, left side high pressure piston 5a and right high pressure piston 5b link to each other with low pressure piston 11's the left and right both ends respectively, and form left high pressure chamber 3a and right high pressure chamber 3b respectively on left side of left high pressure piston 5a and right high pressure piston 5 b's right side, form left low pressure chamber 4a and right low pressure chamber 4b respectively on low pressure piston 11's left side and right side, left side high pressure chamber 3a and right high pressure chamber 3b communicate with high-pressure delivery outlet H through first left check valve 2a and first right check valve 2b respectively. And the left high-pressure cavity 3a and the right high-pressure cavity 3b are respectively communicated with the oil inlet P through a second left check valve 1a and a second right check valve 1 b.
The buffering brake assembly comprises a left one-way sequence valve 6a, a right one-way sequence valve 6b, a left overflow valve 8a and a right overflow valve 8 b.
The hydraulic control reversing valve component comprises a valve body, a control valve core 9 arranged in the cavity of the valve body and end covers arranged at two ends of the control valve core 9; and the left overflow valve 8a, the right overflow valve 8b, the left hydraulic control one-way valve 10a and the right hydraulic control one-way valve 10b are all fixed on the valve body. The hydraulic control reversing valve assembly is characterized in that a plurality of protruding rings arranged at intervals are arranged on the two ends of a reversing valve core 9 and the middle outer circumference of the reversing valve core, a left control cavity 11a and a right control cavity 11B are formed at the left end and the right end of the reversing valve core 9 respectively, and an oil inlet P, an oil return port T, a first oil port A and a second oil port B are arranged on the hydraulic control reversing valve assembly. Wherein, the setting of bellying ring satisfies on the change-over valve core 9: when the reversing valve core 9 moves leftwards, the oil inlet P is communicated with the first oil port A, and the second oil port B is communicated with the oil return port T; when the reversing valve core 9 moves rightwards, the oil inlet P is communicated with the second oil port B, and the first oil port A is communicated with the oil return port T. The specific implementation method comprises the following steps: four protruding rings are sequentially arranged on the reversing valve core 9 from left to right: a left first raised ring 91, a left second raised ring 92, a right second raised ring 93 and a right first raised ring 94, wherein the four raised rings are integrated with the reversing valve core 9. The lower part of the reversing valve core 9 is provided with five oil ports: the first oil return port T1, the first oil port A, the oil inlet P, the second oil port B and the second oil return port T2 are sequentially arranged from left to right, wherein the first oil return port T1 is communicated with the second oil return port T2 to form the oil return port T. When the reversing valve core 9 moves leftwards, the oil inlet P and the first oil port A are communicated between the left second bulge ring 92 and the right second bulge ring, and the second oil port B and the second oil return port T2 are communicated between the right second bulge ring 93 and the right first bulge ring 94; when the direction switch valve core 9 moves to the right, the first oil port a and the first oil return port T1 form communication between the left first bulge loop 91 and the left second bulge loop 92, and the oil inlet P and the second oil port B form communication between the left second bulge loop 92 and the right second bulge loop 93.
The inner walls of the two ends of the left low-pressure cavity 4a and the right low-pressure cavity 4b are respectively provided with a left through-flow groove 7a and a right through-flow groove 7b which are annular, and the diameters of the left through-flow groove 7a and the right through-flow groove 7b are both larger than that of the low-pressure piston 11; the left through-flow groove 7a communicates the left low-pressure chamber 4a with the first oil port A, and the right through-flow groove 7B connects the right low-pressure chamber 4B with the second oil port B. When the low-pressure piston moves to the right, the right through-flow groove is covered, and when the low-pressure piston moves to the left, the left through-flow groove is covered; the left check sequence valve 6a and the right check sequence valve 6B are connected to the left end and the right end of the left low-pressure cavity 4a and the right low-pressure cavity 4B respectively, the left check sequence valve 6a connects the left low-pressure cavity 4a with the first oil port A, and the right check sequence valve 6B connects the right low-pressure cavity 4B with the second oil port B.
An oil inlet of the left overflow valve 8a is communicated with a first oil port A, a left through-flow groove 7a and a left one-way sequence valve 6a, and an oil return port of the left overflow valve is connected with a left control cavity 11a of the hydraulic control reversing valve assembly, an oil inlet of a left hydraulic control one-way valve 10a and a control oil port of a right hydraulic control one-way valve 10 b; and an oil inlet of the right overflow valve 8B is communicated with the second oil port B, the right through-flow groove 7B and the right one-way sequence valve 6B, and an oil return port of the right overflow valve is connected with a right control cavity 11B of the hydraulic control reversing valve assembly, a control oil port of the left hydraulic control one-way valve 10a and an oil inlet of the right hydraulic control one-way valve 10B. And oil return ports of the left pilot-controlled check valve 10a and the right pilot-controlled check valve 10b are communicated with an oil return port of the pilot-controlled check valve assembly. Under the state that the left overflow valve 8a is opened, the right hydraulic control one-way valve 10B is opened, the reversing valve core 9 moves rightwards, the oil inlet P is communicated with the second oil port B, and the first oil port A is communicated with the first oil return port T1; when the right overflow valve 8B is opened, the left hydraulic control check valve 10a is opened, the reversing valve core 9 moves left, the oil inlet P is communicated with the first oil port a, and the second oil port B is communicated with the second oil return port T2.
The working principle and the working process of the invention are as follows:
when the low-pressure piston 11 moves to the right, at the same time, the reversing valve core 9 of the hydraulic control reversing valve component is in a state of communicating the port P with the port A and communicating the port B with the port T2, high-pressure oil enters the left low-pressure cavity 4a through the port A of the hydraulic control reversing valve component to push the low-pressure piston 11 to move to the right, before the low-pressure piston 11 moves to the position that the right through-flow groove 7B is uncovered, the oil in the right piston cavity 4B returns to the port B of the hydraulic control reversing valve assembly through the right through-flow groove 7B, when the low-pressure piston 11 covers the right through-flow groove 7B, as shown in fig. 2, the oil in the right piston chamber 4B can only return to the port B through the sequence valve in the right one-way sequence valve 6B, therefore, the right one-way sequence valve 6b generates braking pressure to the right low-pressure cavity 4b, so that the low-pressure piston 11 is braked and stopped without touching a right end cover so as not to generate noise, and the left overflow valve 8a is triggered to open; when the left overflow valve 8a is opened, oil at the P port enters a left control cavity 11a of the reversing valve core 9 through the left overflow valve 8a, the left control cavity 11a is also connected with a control oil port of a right hydraulic control one-way valve 10B, and the right hydraulic control one-way valve 10B is opened, so that pressure oil in the left control cavity 11a pushes the reversing valve core 9 to move rightwards, the oil in the right control cavity 11B returns to the T port through the right hydraulic control one-way valve 10B, the reversing valve core 9 moves to the right position, and the P port and the B port are communicated, and the A port and the T1 port are communicated; thus, oil enters the right low-pressure chamber 4B through the one-way valves in the port P, the port B and the right one-way sequence valve 6B to push the low-pressure piston 11 to move leftwards.
In the process that the low-pressure piston 11 moves leftwards, after the low-pressure piston 11 opens the right through-flow groove 7B, oil in the port B simultaneously enters the right low-pressure chamber 4B through the right through-flow groove 7B and the one-way valve of the right one-way sequence valve 6B, when the low-pressure piston 11 moves leftwards to cover the left through-flow groove 7a, as shown in fig. 3, the oil in the left piston chamber 4a can only return to the port A through the sequence valve in the left one-way sequence valve 6a, so that brake pressure is generated on the left low-pressure chamber 4a through the left one-way sequence valve 6a, on one hand, the low-pressure piston 11 generates brake stop and cannot touch the left end cover to generate noise, and on the other hand, the right; when the right overflow valve 8B is opened, oil at the P port enters a right control cavity 11B of the reversing valve core 9 through the right overflow valve 8B, the right control cavity 11B is also connected with a control oil port of the left hydraulic control one-way valve 10a, and the left hydraulic control one-way valve 10a is opened, so that pressure oil in the right control cavity 11B pushes the reversing valve core 9 to move leftwards, the oil in the left control cavity 11a returns to the T port through the left hydraulic control one-way valve 10a, the reversing valve core 9 moves to the left position, and the P port is communicated with the A port, the B port and the T2 port; thus, oil enters the left low-pressure chamber 4a through the check valves in the port P, the port A and the left check sequence valve 6a to push the low-pressure piston 11 to move rightwards. This is repeated.
Therefore, the supercharger can reciprocate left and right without noise.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the scope of the present invention, and any modifications and equivalents thereof within the spirit and scope of the present invention are included therein.
Claims (4)
1. A low-noise hydraulic pressure booster comprises a pressure boosting assembly and a hydraulic control reversing valve assembly, wherein the pressure boosting assembly comprises a low-pressure piston, a left high-pressure piston and a right high-pressure piston, the left high-pressure piston and the right high-pressure piston are respectively connected with the left end and the right end of the low-pressure piston, a left high-pressure cavity and a right high-pressure cavity are respectively formed on the left side of the left high-pressure piston and the right side of the right high-pressure piston, a left low-pressure cavity and a right low-pressure cavity are respectively formed on the left side of the low-pressure piston and the right side of the low-pressure piston, and the left high-pressure cavity and the right high-pressure cavity are;
the hydraulic brake is characterized by also comprising a buffer brake assembly, wherein the buffer brake assembly comprises a left one-way sequence valve, a right one-way sequence valve, a left overflow valve and a right overflow valve; wherein,
the hydraulic control reversing valve assembly is characterized in that a plurality of raised rings arranged at intervals are arranged on the outer circumferences of two ends and the middle of a reversing valve core in the hydraulic control reversing valve assembly, a left control cavity and a right control cavity are formed at the left end and the right end of the reversing valve core respectively, and an oil inlet, an oil return opening, a first oil port and a second oil port are arranged on the hydraulic control reversing valve assembly;
the inner walls of two ends of the left low-pressure cavity and the right low-pressure cavity are respectively provided with a left through flow groove and a right through flow groove which are annular, and the diameters of the left through flow groove and the right through flow groove are both larger than that of the low-pressure piston; the left through flow groove communicates the left low-pressure cavity with the first oil port, and the right through flow groove connects the right low-pressure cavity with the second oil port; when the low-pressure piston moves to the right, the right through-flow groove is covered, and when the low-pressure piston moves to the left, the left through-flow groove is covered; the left one-way sequence valve and the right one-way sequence valve are respectively connected to the left end and the right end of the left low-pressure cavity and the right low-pressure cavity, the left one-way sequence valve connects the left low-pressure cavity with the first oil port, and the right one-way sequence valve connects the right low-pressure cavity with the second oil port;
an oil inlet of the left overflow valve is communicated with the first oil port, the left through flow groove and the left one-way sequence valve, and an oil return port of the left overflow valve is connected with a left control cavity of the hydraulic control reversing valve component, an oil inlet of the left hydraulic control one-way valve and a control oil port of the right hydraulic control one-way valve; an oil inlet of the right overflow valve is communicated with the second oil port, the right through flow groove and the right one-way sequence valve, and an oil return port of the right overflow valve is connected with a right control cavity of the hydraulic control reversing valve assembly, a control oil port of the left hydraulic control one-way valve and an oil inlet of the right hydraulic control one-way valve; the oil return ports of the left hydraulic control one-way valve and the right hydraulic control one-way valve are communicated with the oil return port of the hydraulic control reversing valve assembly; when the left overflow valve is in a opened state, the right hydraulic control one-way valve is opened, the reversing valve core moves rightwards, the oil inlet is communicated with the second oil port, and the first oil port is communicated with the oil return port; when the right overflow valve is opened, the left hydraulic control check valve is opened, the reversing valve core moves leftwards, the oil inlet is communicated with the first oil port, and the second oil port is communicated with the oil return port.
2. The low noise hydraulic booster of claim 1, wherein the raised ring on the reversing valve spool is arranged such that: when the reversing valve core moves leftwards, the oil inlet is communicated with the first oil port, and the second oil port is communicated with the oil return port; when the reversing valve core moves rightwards, the oil inlet is communicated with the second oil port, and the first oil port is communicated with the oil return port.
3. The low noise hydraulic booster of claim 1, wherein the left and right high pressure chambers are in communication with the oil inlet through a second left check valve and a second right check valve, respectively.
4. The low-noise hydraulic pressure booster as claimed in claim 1, wherein the hydraulic control directional valve assembly comprises a valve body, a control valve core arranged in the cavity of the valve body and end caps arranged at two ends of the control valve core; and the left overflow valve, the right overflow valve, the left hydraulic control one-way valve and the right hydraulic control one-way valve are all fixed on the valve body.
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| CN201810479398.XA CN108612682B (en) | 2018-05-18 | 2018-05-18 | A kind of low noise hydraulic intensifier |
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| CN201810479398.XA CN108612682B (en) | 2018-05-18 | 2018-05-18 | A kind of low noise hydraulic intensifier |
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| CN108612682B true CN108612682B (en) | 2019-08-27 |
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| CN112324732B (en) * | 2020-11-17 | 2023-01-20 | 中国铁建重工集团股份有限公司 | Electro-hydraulic control system of hydraulic wrench and hydraulic wrench device |
| CN113266610B (en) * | 2021-04-22 | 2023-05-05 | 华侨大学 | Radial plunger hydraulic device adopting hydraulic control check valve for flow distribution and working method |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102287407A (en) * | 2011-09-19 | 2011-12-21 | 宁波汉商液压有限公司 | Double-action reciprocating hydraulic booster |
| CN103613035A (en) * | 2013-11-25 | 2014-03-05 | 武汉船用机械有限责任公司 | Winch hydraulic brake system with boosting function |
| CN106523335A (en) * | 2016-08-25 | 2017-03-22 | 湖南莫尔顿智能勘探机器人有限公司 | Automatic reversing water pump |
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- 2018-05-18 CN CN201810479398.XA patent/CN108612682B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102287407A (en) * | 2011-09-19 | 2011-12-21 | 宁波汉商液压有限公司 | Double-action reciprocating hydraulic booster |
| CN103613035A (en) * | 2013-11-25 | 2014-03-05 | 武汉船用机械有限责任公司 | Winch hydraulic brake system with boosting function |
| CN106523335A (en) * | 2016-08-25 | 2017-03-22 | 湖南莫尔顿智能勘探机器人有限公司 | Automatic reversing water pump |
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| CN108612682A (en) | 2018-10-02 |
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