CN108561344B - Double-acting reciprocating hydraulic pressure booster - Google Patents
Double-acting reciprocating hydraulic pressure booster Download PDFInfo
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- CN108561344B CN108561344B CN201810480250.8A CN201810480250A CN108561344B CN 108561344 B CN108561344 B CN 108561344B CN 201810480250 A CN201810480250 A CN 201810480250A CN 108561344 B CN108561344 B CN 108561344B
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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
Abstract
The invention provides a double-acting reciprocating hydraulic supercharger, which is provided with an oil inlet, a first working oil port, a second working oil port, an oil return port and a high-pressure oil outlet and comprises: the reversing valve comprises a reversing valve core, a left spring, a right spring, a piston, a left plunger, a right plunger, a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve. The double-acting reciprocating hydraulic pressure booster provided by the embodiment of the invention has a simple structure and can achieve high-frequency boosting.
Description
Technical Field
The invention relates to a supercharger, in particular to a double-acting reciprocating hydraulic supercharger capable of reliably and automatically and continuously supercharging.
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, has a complex structure, is large in size and weight, is inconvenient to carry, and is difficult to adopt in the aspects of flammable and explosive occasions and portable machinery.
The invention patent of the hydraulic pressure booster with the publication number of CN101666339A provides a proposal for controlling the continuous movement of a pressure cylinder by using a stroke control reversing valve and a main reversing valve, which has innovation compared with the traditional domestic double-acting pressure booster using an electromagnetic reversing valve to control the reversing, but also has the following defects:
(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, the chain is broken, and 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 whole structure is complex, and the processing cost is high.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the technical problems in the related art.
To this end, an object of the present invention is to propose a double-acting reciprocating hydraulic supercharger which is simple in structure and capable of achieving high-frequency supercharging.
According to the double-acting reciprocating hydraulic pressure booster of the embodiment of the invention, the booster is provided with an oil inlet, a first working oil port, a second working oil port, an oil return port and a high-pressure oil outlet, and the double-acting reciprocating hydraulic pressure booster comprises: the hydraulic control system comprises a reversing valve core, a left spring, a right spring, a piston, a left plunger, a right plunger, a first check valve, a second check valve, a third check valve and a fourth check valve, wherein a left cavity which is communicated with the left end face of the reversing valve core leftwards and a right cavity which is communicated with the right end face of the reversing valve core rightwards are arranged in the reversing valve core, the left cavity is provided with a first through hole communicated with a second working oil port, the right cavity is provided with a second through hole communicated with the oil inlet selectively and a third through hole communicated with the oil return port selectively, a left control cavity communicated with the left cavity and a right control cavity communicated with the right cavity are arranged on a supercharger, the left spring is arranged in the left control cavity, the right end of the left spring is abutted against the left end of the reversing valve core, the right spring is arranged in the right control cavity, the left end of the right spring is abutted against the right end of the reversing valve core, the first working oil port is connected with the left piston cavity, the second working oil port is connected with the right piston cavity, the oil inlet is connected with the left plunger cavity through the first one-way valve and is connected with the right plunger cavity through the second one-way valve, the left plunger cavity is connected with the high-pressure oil outlet through the third one-way valve and is connected with the right plunger cavity through the fourth one-way valve.
Advantageously, when the second through-flow hole is communicated with the oil inlet and the third through-flow hole is isolated from the oil return opening, the oil inlet is communicated with the second working oil opening and the first working oil opening is communicated with the oil return opening.
Advantageously, when the second through-flow hole is isolated from the oil inlet and the third through-flow hole is communicated with the oil return opening, the oil inlet is communicated with the first working oil port and the second working oil port is communicated with the oil return opening.
Advantageously, the left cavity has a left damping hole therein communicating the left cavity with the left control chamber, and the right cavity has a right damping hole therein communicating the right cavity with the right control chamber.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
FIG. 1 is a cross-sectional view of a double acting reciprocating hydraulic pressure intensifier in accordance with an embodiment of the present invention;
FIG. 2 is a left side view of FIG. 1;
FIG. 3 is a cross-sectional view taken along line C-C of FIG. 1;
FIG. 4 is a cross-sectional view taken along line D-D of FIG. 1;
FIG. 5 is a cross-sectional view taken along line E-E of FIG. 1;
fig. 6 is a partially enlarged schematic view of F in fig. 1.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
A double-acting reciprocating hydraulic pressure intensifier according to an embodiment of the present invention is described in detail below with reference to the accompanying drawings.
As shown in fig. 1 to 6, a double-acting reciprocating hydraulic pressure booster according to an embodiment of the present invention, the booster having an oil inlet P, a first working oil port a, a second working oil port B, an oil return port T, and a high-pressure oil outlet H, includes: the reversing valve comprises a reversing valve core 7, a left spring 9.1, a right spring 9.2, a piston 2, a left plunger 3.1, a right plunger 3.2, a first one-way valve 4.1, a second one-way valve 4.2, a third one-way valve 5.1 and a fourth one-way valve 5.2.
Specifically, the direction change valve body 7 has a left cavity 7.1 extending through a left end surface of the direction change valve body 7 in the left direction and a right cavity 7.2 extending through a right end surface of the direction change valve body 7 in the right direction.
The left cavity 7.1 is provided with a first through flow hole 7a communicated with the second working oil port B, the right cavity 7.2 is provided with a second through flow hole 7B selectively communicated with the oil inlet P, the right cavity 7.2 is provided with a third through flow hole 7c selectively communicated with the oil return port T, and the supercharger is provided with a left control cavity 6a communicated with the left cavity 7.1 and a right control cavity 6B communicated with the right cavity 7.2.
The left spring 9.1 is arranged in the left control cavity 6a, the right end of the left spring 9.1 abuts against the left end of the reversing valve core 7, the right spring 9.2 is arranged in the right control cavity 6b, and the left end of the right spring 9.2 abuts against the right end of the reversing valve core 7.
The first working oil port A is connected with the left piston cavity 2a, and the second working oil port B is connected with the right piston cavity 2B.
The oil inlet P is connected with the left plunger cavity 6c through a first one-way valve 4.1 and the oil inlet P is connected with the right plunger cavity 6d through a second one-way valve 4.2.
The left plunger cavity 6c is connected with the high-pressure oil outlet H through a third one-way valve 5.1, and the right plunger cavity 6d is connected with the high-pressure oil outlet H through a fourth one-way valve 5.2.
According to an embodiment of the present invention, when the second through-flow hole 7B communicates with the oil inlet P and the third through-flow hole 7c is blocked from the oil return port T, the oil inlet P communicates with the second working port B and the first working port a communicates with the oil return port T. Advantageously, when the second flow-through hole 7B is blocked from the oil inlet P and the third flow-through hole 7c is communicated with the oil return port T, the oil inlet P is communicated with the first working port a and the second working port B is communicated with the oil return port T.
According to a specific example of the present invention, the left cavity 7.1 has a left orifice 8.1 therein communicating the left cavity 7.1 with the left control chamber 6a, and the right cavity 7.2 has a right orifice 8.2 therein communicating the right cavity 7.2 with the right control chamber 6 b.
The operation of a double-acting reciprocating hydraulic intensifier according to an embodiment of the present invention is briefly described as follows:
in practical application, the oil inlet P can be connected with the outlet of a hydraulic pump, the oil return port T is connected with an oil tank, and the high-pressure oil outlet H is connected with a working oil cylinder or other execution elements.
The reversing valve core 7, the left spring 9.1 and the right spring 9.2 jointly form an automatic reversing valve component. The automatic reversing valve component can slide left and right to switch an oil way according to the pressure difference between the oil inlet P and the second working oil port B and the pressure difference between the second working oil port B and the oil return port T, and further controls the piston 2 to drive the left plunger 3.1 and the right plunger 3.2 to reciprocate left and right to pressurize.
Before oil enters the oil inlet P, the valve core 7 is in an initial position shown in figure 1 under the action of the left spring 9.1 and the right spring 9.2, the second through flow hole 7b is communicated with the oil inlet P, and the third through flow hole 7C is communicated with the oil return port T.
When the oil enters the oil inlet P, the oil enters the right control cavity 6B through the second through-flow hole 7B and the right damping hole 8.2, the oil in the left control cavity 6a flows into the second working oil port B through the first damping hole 8.1 and the first through-flow hole 7a, the reversing valve element 7 starts to move leftwards under the pressure difference between the oil inlet P and the second working oil port B (at this time, the left spring 9.1 is compressed and the right spring 9.2 is stretched), the third through-flow hole 7c is gradually separated from the oil return port T, the second through-flow hole 7B is communicated with the oil inlet P, the pressure of the right control cavity 6B is increased and finally equals to the pressure of the oil inlet P, when the reversing valve element 7 moves to the left end position, the oil inlet P is communicated with the second working oil port B, the first working oil port A is communicated with the oil return port T, the oil enters the right piston cavity 2B from the oil inlet P through the second working oil port B, the piston 2 starts to move leftwards, the oil return port T flows back to the oil tank. Meanwhile, oil in the oil inlet P enters the right plunger cavity 6d through the second one-way valve 4.2, and the oil in the left plunger cavity 6c is pressurized and then discharged to the high-pressure oil outlet H through the third one-way valve 5.1.
When the piston 2 moves to the left, the oil does not flow any more. The pressure difference between the oil inlet P and the second working oil port B disappears, the reversing valve core 7 starts to move rightwards under the acting force of a left spring 9.1 (the left spring 9.1 pushes rightwards to restore the original state) and a right spring 9.2 (the spring 9.2 pulls rightwards to restore the original state), in the process of moving rightwards, a third through-flow hole 7c is communicated with the oil return port T to ensure that the pressure of a right control cavity 6B is less than that of a left control cavity 6a, the reversing valve core 7 continuously moves rightwards to the right end position, at the moment, the second through-flow hole 7B is separated from the oil inlet P, the third through-flow hole 7c is communicated with the oil return port T, the pressure of the right control cavity 6B is equal to that of the oil return port T, the oil inlet P is communicated with the first working oil port A, the second working oil port B is communicated with the oil return port T, the pressure difference between the second working oil port B and the oil return port T, the piston 2 starts to move rightwards, oil in the right piston cavity 2B flows back to the oil tank through the second working oil port B and the oil return port T, meanwhile, the oil in the oil inlet P enters the left plunger cavity 6c through the first check valve 4.1, and the oil in the right plunger cavity 6d is discharged to the high-pressure oil outlet H through the fourth check valve 5.2 after being pressurized.
When the piston 2 moves to the head rightwards, the oil does not flow to the second working oil port B and the pressure difference between the oil return ports T disappears, the reversing valve core 7 starts to move leftwards to the initial position under the acting force of the left spring 9.1 and the right spring 9.2, so that circulation is formed, and the piston 2 automatically reciprocates back and forth to pressurize without electric control under the control of the invention.
The double-acting reciprocating hydraulic pressure booster according to the embodiment of the invention has the advantages of simple structure, compact volume and low processing cost, can automatically perform reciprocating pressurization, and does not need electric control.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although the embodiments of the present invention have been shown and described, it is understood that the embodiments are illustrative and not restrictive, and that those skilled in the art may make changes, modifications, substitutions and alterations to the embodiments without departing from the scope of the present invention.
Claims (2)
1. The utility model provides a reciprocating type hydraulic pressure booster of two effects, oil inlet, first work hydraulic fluid port, second work hydraulic fluid port, oil return opening, high-pressure oil-out have on the booster, its characterized in that includes: the hydraulic control system comprises a reversing valve core, a left spring, a right spring, a piston, a left plunger, a right plunger, a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve, wherein a left cavity which is communicated with the left end face of the reversing valve core leftwards and a right cavity which is communicated with the right end face of the reversing valve core rightwards are arranged in the reversing valve core, the left cavity is provided with a first through hole communicated with a second working oil port, the right cavity is provided with a second through hole selectively communicated with the oil inlet and a third through hole selectively communicated with the oil return port, a left control cavity communicated with the left cavity and a right control cavity communicated with the right cavity are arranged on a supercharger, the left spring is arranged in the left control cavity, the right end of the left spring is abutted against the left end of the reversing valve core, the right spring is arranged in the right control cavity, the left end of the right spring is abutted against the right end of the reversing valve core, the first working oil port is connected with the left piston cavity, the second working oil port is connected with the right piston cavity, the oil inlet is connected with the left plunger cavity through the first one-way valve and is connected with the right plunger cavity through the second one-way valve, the left plunger cavity is connected with the high-pressure oil outlet through the third one-way valve and the right plunger cavity is connected with the high-pressure oil outlet through the fourth one-way valve, when the second through-flow hole is communicated with the oil inlet and the third through-flow hole is isolated from the oil return port, the oil inlet P is communicated with the second working oil port, the first working oil port is communicated with the oil return port, when the second through-flow hole is isolated from the oil inlet and the third through-flow hole is communicated with the oil return opening, the oil inlet is communicated with the first working oil port, and the second working oil port is communicated with the oil return port.
2. The double acting reciprocating hydraulic booster of claim 1, wherein the left cavity has a left orifice therein communicating the left cavity with the left control chamber and the right cavity has a right orifice therein communicating the right cavity with the right control chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810480250.8A CN108561344B (en) | 2018-05-18 | 2018-05-18 | Double-acting reciprocating hydraulic pressure booster |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810480250.8A CN108561344B (en) | 2018-05-18 | 2018-05-18 | Double-acting reciprocating hydraulic pressure booster |
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| Publication Number | Publication Date |
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| CN108561344A CN108561344A (en) | 2018-09-21 |
| CN108561344B true CN108561344B (en) | 2020-03-27 |
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| CN201810480250.8A Active CN108561344B (en) | 2018-05-18 | 2018-05-18 | Double-acting reciprocating hydraulic pressure booster |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109611305B (en) * | 2018-12-01 | 2020-02-21 | 东营盛昶石油机械有限公司 | Booster water pump |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2346977Y (en) * | 1997-05-23 | 1999-11-03 | 顾新华 | Ultrahigh pressure hydraulic dual-action continuous automatic supercharger |
| DE10158181C1 (en) * | 2001-11-28 | 2003-05-28 | Minibooster Hydraulics As Soen | Hydraulic pressure intensifier comprises a supply connection, a return connection, a high pressure connection, a piston arrangement, a switching valve arrangement |
| DE10393780T5 (en) * | 2002-11-25 | 2005-10-27 | Hartho-Hydraulic Aps | Verstärkerbaueinheit |
| CN203272273U (en) * | 2013-05-14 | 2013-11-06 | 河南黄河旋风股份有限公司 | Novel double-acting supercharger |
| CN107023531A (en) * | 2016-02-02 | 2017-08-08 | 黄石市君和机电科技有限公司 | A kind of self-action booster |
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Effective date of registration: 20200228 Address after: 201500 403-2, No. 30, Gaolin Road, Zhuxing Town, Jinshan District, Shanghai Applicant after: SHANGHAI SHUNNUO MACHINERY CO., LTD. Address before: 523000 Dongguan City, Guangdong Province, Songshan Lake High-tech Industrial Development Zone Headquarters, No. 2, No. 1 District, No. 2, No. 201 Applicant before: Dongguan hate Paavo Hydraulic Technology Co., Ltd. |
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