CN108167261B - Hydraulic reciprocating driving mechanism and hydraulic reciprocating driving pump - Google Patents
Hydraulic reciprocating driving mechanism and hydraulic reciprocating driving pump Download PDFInfo
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- CN108167261B CN108167261B CN201711170432.7A CN201711170432A CN108167261B CN 108167261 B CN108167261 B CN 108167261B CN 201711170432 A CN201711170432 A CN 201711170432A CN 108167261 B CN108167261 B CN 108167261B
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/202—Externally-operated valves mounted in or on the actuator
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention discloses a hydraulic reciprocating driving mechanism and a hydraulic reciprocating driving pump, wherein the hydraulic reciprocating driving mechanism comprises: the piston shell is internally provided with a hydraulic chamber; a piston disposed in the hydraulic chamber of the piston housing and separating the hydraulic chamber into a first hydraulic chamber, a second hydraulic chamber, and a third hydraulic chamber; a hydraulic system which feeds low pressure fluid to the first hydraulic chamber and high pressure fluid to the second hydraulic chamber, the hydraulic system being actuatable to: under a first preset working condition, low-pressure liquid is introduced into the third hydraulic chamber, and the piston moves towards the first direction; and under a second preset working condition, high-pressure liquid is introduced into the third hydraulic chamber, the piston moves towards a second direction, and the second direction is opposite to the first direction. The hydraulic reciprocating driving mechanism and the hydraulic reciprocating driving pump have the advantages of compact structure, small volume, light weight, simple driving mode, capability of realizing automatic reversing, few easily-damaged parts and low operation cost.
Description
Technical Field
The invention relates to the technical field of structural design of pumps, in particular to a hydraulic reciprocating driving mechanism and a hydraulic reciprocating driving pump.
Background
Currently, in the field of reciprocating pump applications, the most widely used is the three-cylinder single-acting piston reciprocating pump. Fig. 1 and 2 are schematic diagrams of the operation of a three-cylinder single-acting piston pump which is widely used at present. Driven by the power source on the right side of fig. 1, the three pistons H of the reciprocating pump reciprocate left and right at different phases. The "T" shaped element in the figure is a one-way valve D which will open or close automatically with the movement of the piston H. The three-cylinder single-action reciprocating pump with the structure mostly adopts the motion principle of a crankshaft connecting rod, cannot adopt hydraulic drive, cannot automatically reverse, and has the advantages of complex mechanical structure, large volume, low mechanical efficiency, easy abrasion of moving parts and high maintenance cost.
Accordingly, the applicant has sought to provide a hydraulic reciprocating drive mechanism and a hydraulic reciprocating drive pump.
Disclosure of Invention
The invention aims to provide a hydraulic reciprocating driving mechanism and a hydraulic reciprocating driving pump, which have the advantages of simple structure, small volume, simple driving mode and high mechanical efficiency.
The technical scheme provided by the invention is as follows:
a hydraulic reciprocating drive mechanism comprising: the piston shell is internally provided with a hydraulic chamber; a piston disposed in a hydraulic chamber of the piston housing and separating the hydraulic chamber into a first hydraulic chamber, a second hydraulic chamber, and a third hydraulic chamber; a hydraulic system that passes low pressure fluid to the first hydraulic chamber and high pressure fluid to the second hydraulic chamber, the hydraulic system being actuatable to: under a first preset working condition, low-pressure liquid is introduced into the third hydraulic chamber, the first hydraulic chamber is communicated with the third hydraulic chamber, and the high-pressure liquid in the second hydraulic chamber pushes the piston to move towards a first direction; under a second preset working condition, high-pressure liquid is introduced into the third hydraulic chamber, the piston is pushed by the high-pressure liquid in the second hydraulic chamber and the third hydraulic chamber to move towards a second direction, and the second direction is opposite to the first direction.
Preferably, the first hydraulic chamber, the second hydraulic chamber and the third hydraulic chamber are arranged in sequence, and the second hydraulic chamber is positioned between the first hydraulic chamber and the third hydraulic chamber; the first direction is a direction in which the first hydraulic chamber points to the second hydraulic chamber, and the second direction is a direction in which the second hydraulic chamber points to the first hydraulic chamber.
Preferably, the piston comprises a first acting part, a first driving part, a second driving part and a second acting part which are sequentially arranged, wherein the radial sizes of the first acting part, the first driving part and the second driving part are sequentially increased, and the radial sizes of the first acting part and the second acting part are the same; the hydraulic chamber of the piston shell comprises a first section, a second section, a third section, a fourth section and a fifth section which are sequentially arranged, wherein the radial size of the third section is smaller than that of the second section and the fourth section; the first driving part is arranged at a third section of the hydraulic chamber in a sealing and sliding manner and separates the second section from the fourth section, and the second section is the first hydraulic chamber; the second driving part is arranged at the fourth section of the hydraulic chamber in a sealing and sliding manner and divides the fourth section into a second hydraulic chamber and a third hydraulic chamber; the first acting part is arranged at the first section of the hydraulic chamber in a sealing and sliding manner, and the second acting part is arranged at the fifth section of the hydraulic chamber in a sealing and sliding manner.
Preferably, the hydraulic system comprises a low pressure fluid output in direct communication with the first hydraulic chamber and a high pressure fluid output in direct communication with the second hydraulic chamber.
Preferably, the hydraulic system further comprises a two-position three-way valve including a first oil port communicating with the first hydraulic chamber, a second oil port communicating with the second hydraulic chamber, and a third oil port communicating with the third hydraulic chamber; under a first preset working condition, the first oil port is communicated with the third oil port; and under a second preset working condition, the second oil port is communicated with the third oil port.
Preferably, the two-position three-way valve is located inside the piston, and the piston is provided with a first oil path, a second oil path and a third oil path; one port of the first oil path is communicated with the first hydraulic chamber, and the other port of the first oil path is communicated with the first oil port; one port of the second oil path is communicated with the second hydraulic chamber, and the other port of the second oil path is communicated with the second oil port; one port of the third oil passage is communicated with the third hydraulic chamber, and the other port of the third oil passage is communicated with the third oil port.
Preferably, the two-position, three-way valve includes a valve housing and a valve spool; the valve core comprises a fixed part and a sliding part, the sliding part comprises a first section, a second section, a third section and a fourth section which are sequentially arranged along a first direction, the outer diameters of the first section, the second section and the third section of the sliding part are gradually reduced, the outer diameters of the second section and the fourth section of the sliding part are equal, a stepped through hole is arranged in the sliding part, the aperture of the first section of the stepped through hole is larger than that of the second section of the stepped through hole, and the first section of the stepped through hole is hermetically and slidably arranged outside the fixed part along the first direction; the inner cavity of the valve casing comprises a first section and a second section which are sequentially arranged along a first direction, the radial size of the first section of the valve casing is larger than that of the second section of the valve casing, the first section and the second section of the valve casing are positioned on two sides of the first oil port, and the second oil port and the third oil port are arranged at the second section of the valve casing; the first section of sliding part is sealed to be slided and is located the first section of valve casing, the second section and the fourth section of sliding part are sealed to be slided and are located the second section of valve casing.
A fourth oil path is arranged on the piston, a fourth oil port is arranged on the second section of the valve shell, one port of the fourth oil path is communicated with the second hydraulic chamber, the other port of the fourth oil path is communicated with the fourth oil port, and the fourth oil path is always communicated with an inner cavity of the valve shell positioned on one side of the valve core; a fifth oil passage is arranged on the piston, a fifth oil port is arranged on the first section of the valve shell, and one port of the fifth oil passage is communicated with the fifth oil port; when the other port of the fifth oil path is communicated with the first hydraulic chamber, the sliding part moves along a second direction, and the first oil port is communicated with the third oil port; when the other port of the fifth oil passage communicates with the second hydraulic chamber, the sliding portion moves in the first direction, and the second oil port communicates with the third oil port.
The invention also discloses a hydraulic reciprocating pump, comprising: the hydraulic reciprocating drive mechanism; the pump shell is arranged outside the piston shell, a first working cavity is arranged in the pump shell, and the first end of the piston acts on the first working cavity; under a first preset working condition, the first working cavity sucks working liquid; and under a second preset working condition, the first working cavity discharges working liquid.
Preferably, a first check valve and a second check valve are arranged on the first working cavity, and the first check valve and the second check valve are arranged on different sides of the first working cavity; under a first preset working condition, the first one-way valve is opened, and the second one-way valve is closed; under a second preset working condition, the first one-way valve is closed, and the second one-way valve is opened.
Preferably, a second working cavity is further arranged in the pump shell, the second working cavity and the first working cavity are symmetrically arranged, and the second end of the piston acts on the second working cavity; under a first preset working condition, the second working chamber discharges working liquid; under a second preset working condition, the second working chamber sucks working liquid, a third one-way valve and a fourth one-way valve are arranged on the second working chamber, the third one-way valve and the fourth one-way valve are respectively arranged on different sides of the second working chamber, the third one-way valve and the first one-way valve are located on the same side, and the fourth one-way valve and the second one-way valve are located on the same side; under a first preset working condition, the third one-way valve is closed, and the fourth one-way valve is opened; and under the second preset working condition, the third one-way valve is opened, and the fourth one-way valve is closed.
The hydraulic reciprocating driving mechanism and the hydraulic reciprocating driving pump provided by the invention can bring at least one of the following beneficial effects:
1. the hydraulic reciprocating driving mechanism of the invention respectively leads low-pressure liquid into the first hydraulic chamber and high-pressure liquid into the second hydraulic chamber through the hydraulic system, and can move the piston to two different directions when the low-pressure liquid and the high-pressure liquid are led into the third hydraulic chamber respectively.
2. In the invention, the first hydraulic chamber, the second hydraulic chamber and the third hydraulic chamber are sequentially arranged, wherein only the third hydraulic chamber is a variable hydraulic chamber, and thrust in different directions is generated among the three hydraulic chambers by adjusting the pressure of hydraulic oil in the third hydraulic chamber so as to drive the piston to move towards two directions.
3. In the invention, the piston and the piston shell are both designed into step structures with different diameters, so that the hydraulic stress surface of the piston is determined, and under the specific piston structure, as long as the oil pressure in the first hydraulic chamber is less than the oil pressure in the second hydraulic chamber, the low-pressure oil or the high-pressure oil is introduced into the third hydraulic chamber to determine that the piston moves towards two different directions, namely, the end surface area of the piston and the end surface area of the piston shell are proportional, so that the working parameters of the hydraulic reciprocating driving mechanism are determined, therefore, the proportional values can be designed according to different application scenes, different users or different application working conditions, and the like, so that the optimized working efficiency of the product is achieved, and the series and batch production of the product with individual and different working parameters can be carried out.
4. According to the invention, the hydraulic system regulates the hydraulic oil introduced into the third hydraulic chamber through the two-position three-way valve, the two-position three-way valve can be arranged outside the piston shell, and the external structure of the reversing valve can be independently designed into a module and is easy to replace.
5. According to the invention, the hydraulic system regulates the hydraulic oil introduced into the third hydraulic chamber through the two-position three-way valve, and the two-position three-way valve can also be arranged in the piston, so that the structure of the total mechanism is more compact, the occupied volume is smaller, and the safety performance is better.
6. According to the invention, when the two-position three-way valve is arranged in the piston, an oil path communicated with the two-position three-way valve is arranged on the piston, and an oil port communicated with the hydraulic chamber is arranged, and when the piston moves, the oil port is communicated with the first hydraulic chamber or the second hydraulic chamber, so that the switching of the two-position three-way valve is driven, the switching of the moving direction of the piston is further controlled, the automatic reciprocating reversing of the piston is realized, and the control mode of the driving mechanism is further simplified.
Drawings
The above features, technical features, advantages and modes of realisation of the present invention will be further described in the following detailed description of preferred embodiments thereof, which is to be read in connection with the accompanying drawings.
FIG. 1 is a front view of the operating principle of a prior art three-cylinder single-acting piston pump;
FIG. 2 is a top plan view of the operating principle of the three-cylinder single-acting piston pump shown in FIG. 1;
FIG. 3 is a schematic diagram of the operation of one embodiment of the hydraulic reciprocating drive mechanism and hydraulic reciprocating drive pump of the present invention under a first predetermined operating condition;
FIG. 4 is a schematic diagram of the operation of the hydraulic reciprocating drive mechanism and the hydraulic reciprocating drive pump shown in FIG. 3 under a second predetermined operating condition;
FIG. 5 is a schematic diagram of the operation of the two-position three-way valve of the hydraulic reciprocating drive mechanism shown in FIG. 3 under a first predetermined condition;
FIG. 6 is a schematic diagram of the operation of the two-position three-way valve of the hydraulic reciprocating drive mechanism shown in FIG. 4 under a second predetermined condition;
FIG. 7 is a schematic structural view of the hydraulic reciprocating drive mechanism and the hydraulic reciprocating drive pump shown in FIG. 3 under a first predetermined operating condition;
FIG. 8 is a schematic diagram of the hydraulic reciprocating drive mechanism and hydraulic reciprocating drive pump shown in FIG. 7 under a second predetermined operating condition.
The reference numbers illustrate:
the hydraulic control device comprises a piston shell 1, a first hydraulic chamber A ', a low-pressure port T, a second hydraulic chamber B ', a high-pressure port P, a third hydraulic chamber C ', a piston 2, a first acting part 21, a first driving part 22, a second driving part 23, a second acting part 24, a two-position three-way valve 3, a valve shell 31, a first oil port A, a second oil port B, a third oil port C, a fifth oil port F, a valve core 32, a fixing part 321, a sliding part 322, a pump shell 4, a first working cavity 41, a second working cavity 42, a first check valve 43, a water inlet cavity 51 and a water outlet cavity 52.
Direction of movement of piston or spool
Direction of flow of high pressure liquid
Direction of flow of low pressure liquid
Direction of flow of working fluid
Detailed Description
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following description will be made with reference to the accompanying drawings. It is obvious that the drawings in the following description are only some examples of the invention, and that for a person skilled in the art, other drawings and embodiments can be derived from them without inventive effort. For the sake of simplicity, the drawings only show schematically the parts relevant to the invention, and they do not represent the actual structure as a product.
As shown in fig. 3 and 4, the present embodiment discloses a hydraulic reciprocating driving mechanism, which comprises a piston housing 1, a piston 2 and a hydraulic system (not shown), wherein a hydraulic chamber is arranged in the piston housing 1, the piston 2 is arranged in the hydraulic chamber of the piston housing 1, and the hydraulic chamber is divided into a first hydraulic chamber a ', a second hydraulic chamber B ' and a third hydraulic chamber C ' which are arranged from left to right. In this embodiment, the hydraulic system includes a low pressure fluid output and a high pressure fluid output, the low pressure fluid output directly delivers the low pressure fluid to the first hydraulic chamber a 'through the low pressure port T on the first hydraulic chamber a', and the high pressure fluid output directly delivers the high pressure fluid to the second hydraulic chamber B 'through the high pressure port P on the second hydraulic chamber B'.
The hydraulic system may be actuated to: under a first preset condition as shown in fig. 3, the third hydraulic chamber C' is filled with low-pressure liquid, and the piston 2 moves in a first direction (i.e., a direction from left to right as shown in fig. 3); under a second preset condition as shown in fig. 4, the third hydraulic chamber C' is filled with high-pressure liquid, and the piston 2 moves in a second direction (i.e., a direction from right to left as shown in fig. 4).
In this embodiment, the piston 2 includes a first acting portion 21, a first driving portion 22, a second driving portion 23 and a second acting portion 24, which are sequentially arranged, the radial dimensions of the first acting portion 21 and the second acting portion 24 are the same, wherein the radial dimensions of the first acting portion 21, the first driving portion 22 and the second driving portion 23 are respectively D3, D2 and D1, and D3, D2 and D1 are sequentially increased. The hydraulic chamber of the piston shell 1 is a first section, a second section, a third section, a fourth section and a fifth section which are sequentially arranged, the radial size of the third section is smaller than that of the second section and the fourth section, the first driving part 22 is hermetically and slidably arranged at the third section of the hydraulic chamber and separates the second section from the fourth section, and the second section is a first hydraulic chamber A'; the second driving part 23 is arranged at the fourth section of the hydraulic chamber in a sealing and sliding manner, and divides the fourth section into a second hydraulic chamber B 'and a third hydraulic chamber C'; the first acting part 21 is arranged at the first section of the hydraulic chamber in a sealing and sliding way, and the second acting part 24 is arranged at the fifth section of the hydraulic chamber in a sealing and sliding way.
As shown in fig. 4, the hydraulic system further comprises a two-position, three-way valve 3 located inside the piston 2. As shown in fig. 5 and 6, the piston 2 is provided with a first oil path, a second oil path and a third oil path, and the two-position three-way valve 3 includes a first oil port a, a second oil port B and a third oil port C. One port of the first oil way is communicated with the first hydraulic chamber A', and the other port of the first oil way is communicated with the first oil port A; one port of the second oil way is communicated with the second hydraulic chamber B', and the other port of the second oil way is communicated with the second oil port B; one port of the third oil passage is communicated with the third hydraulic chamber C', and the other port is communicated with the third port C. Under a first preset working condition, the first oil port A is communicated with the third oil port C; and under a second preset working condition, the second oil port B is communicated with the third oil port C.
Specifically, the two-position three-way valve 3 includes a valve housing 31 and a valve spool 32. Wherein the valve housing 31 is integrally formed with the piston 2, the valve core 32 includes a fixing portion 321 and a sliding portion 322, the sliding portion 322 includes a first section and a second section sequentially arranged along a first direction (from left to right as shown in fig. 4 and 5), the outer diameters of the first section, the second section and the third section of the sliding part 322 are gradually reduced, the outer diameters of the second section and the fourth section of the sliding part 322 are equal to each other and are D4, the outer diameter of the first section is D5, a stepped through hole is arranged in the sliding part 322, the aperture of the first section (the left half part of the stepped through hole shown in FIG. 6) of the stepped through hole is larger than that of the second section (the right half part of the stepped through hole shown in FIGS. 5 and 6), the first section through hole of the stepped through hole along the first direction (i.e. the direction from left to right shown in FIGS. 5 and 6) is hermetically and slidably arranged outside the fixing part 321, and the outer diameter of the fixing part 321 is D6. The inside cavity of valve casing 31 includes first section and the second section of following the first direction and arranging in proper order, and the radial dimension of first section of valve casing 31 is greater than its second section, and first section and the second section of valve casing 31 are located first hydraulic fluid port A's both sides, and the second section department of valve casing 31 is equipped with second hydraulic fluid port B and third hydraulic fluid port C. The first section of the sliding part 322 is sealingly slidably provided in the first section of the valve housing 31, and the second section and the fourth section of the sliding part 322 are sealingly slidably provided in the second section of the valve housing 31.
Specifically, a fourth oil path is provided on the piston 2, a fourth oil port is provided on the second section of the valve housing 31, a port of the fourth oil path is communicated with the second hydraulic chamber B ', another port is communicated with the fourth oil port, and the fourth oil path is communicated with the internal cavity of the valve housing 31 located on one side of the valve element 32 all the time, that is, the high-pressure liquid in the second hydraulic chamber B' is communicated with the fourth oil port on the valve housing 31 through the fourth oil path on the piston 2, and enters the internal cavity of the valve housing 31 located on one side of the valve element 32 through the fourth oil port, so that the high-pressure liquid is introduced into the internal cavity of the valve housing 31 located on one side of the valve element 32 (i.e., the right cavity of the valve housing 31 shown in fig. 5 and 6) all the time. Specifically, a fifth oil passage is formed in the piston 2, a fifth oil port F is formed in the first section of the valve housing 31, one port of the fifth oil passage is communicated with the fifth oil port F, and along with the movement of the piston, the other port F ' of the fifth oil passage is respectively communicated with the first hydraulic chamber a ' and the second hydraulic chamber B '.
The specific working process of the hydraulic reciprocating drive mechanism of the present embodiment is as follows:
fig. 3 and 5 show a first preset condition of the hydraulic reciprocating driving mechanism, when another port of the fifth oil path (i.e., the port F ' shown in fig. 3) is communicated with the first hydraulic chamber a ', the low-pressure liquid in the first hydraulic chamber a ' flows through the fifth oil path to the first section of the valve housing 31 and enters the valve housing 31 through the fifth oil port F of the valve housing 31, at this time, the left end chamber of the valve element 32 is in a low-pressure state, and the right end chamber of the valve element 32 is always connected to the fourth oil port connected to the second hydraulic chamber B ', so that the high-pressure state is always maintained, the first oil port a and the third oil port C are communicated with each other and both communicated with the first hydraulic chamber a ', the low-pressure state is maintained, and when the hydraulic pressure is F ═ pS ═ p ═ (D4 ═ pi (D4)2-D62) /4) the slide 322 in the spool 32 moves to the left to the position shown in fig. 5.
At this time, the first port a and the third port C are communicated with each other and both lead to the low pressure port T of the piston housing 1, and at this time, the passage between the second port B and the third port C is blocked by the cylindrical surface of the fourth section of the sliding portion 322, and the oil path is blocked. Since the first port a is communicated with the first hydraulic chamber a 'through the first oil path on the piston 2, and the third port C is communicated with the third hydraulic chamber C through the third oil path on the piston 2, when the first port a and the third port C in the two-way three-way valve are communicated, the first hydraulic chamber a' and the third hydraulic chamber C 'in the piston housing are communicated, and the low-pressure liquid flows into the third hydraulic chamber C' from the first hydraulic chamber a ', so as to form the movement oil path of the piston 2 shown in fig. 3, at this time, the first hydraulic chamber a' and the third hydraulic chamber C 'are both in a low-pressure state, the second hydraulic chamber B' is in a high-pressure state, and the movement oil path is pushed by the hydraulic pressure (the hydraulic pressure is F ═ pS ═ p pi (D1)2-D22) And/4), the piston moves rightward (i.e., in the first direction) as a whole. The two-position three-way valve 3 can effectively reduce the impact force of the valve element 32 in the direction change by F pS p pi D4 by setting the valve element 32 to the fixed portion 321 and the sliding portion 3222The reduction of/4 is F-pS-p pi (D4)2-D62)/4。
Fig. 4 and 6 show a second preset condition of the hydraulic reciprocating driving mechanism, when the piston 2 is driven by the hydraulic oil to move to the right to the position shown in fig. 4, another port (i.e. the port F' shown in fig. 4) of the fifth oil path on the piston 2 and the other port are connected with the hydraulic oil pathThe second hydraulic chamber B 'is communicated, the high-pressure oil in the second hydraulic chamber B' flows to the first section of the valve housing 31 through the fifth oil path and enters the valve housing 31 through the fifth oil port F of the valve housing 31, at this time, the left chamber of the valve element 32 is in a high-pressure state, and the first oil port a on the valve housing 31 is connected with the first oil path on the piston 2 to maintain a low pressure, the second oil port B and the third oil port C are communicated with each other and are both communicated with the second hydraulic chamber B ', the high-pressure state is maintained, the right chamber of the valve element 32 is communicated with the second hydraulic chamber B' through the fourth oil path to maintain a high-pressure state, and the hydraulic pressure is maintained at the hydraulic pressure (the hydraulic pressure is F pS p (D5)2-D42) 4) moves to the right to the position shown in fig. 6.
At this time, the second port B and the third port C are communicated with each other and both lead to the high pressure port P of the piston housing 1, and at this time, the passage between the first port a and the third port C is blocked by the cylindrical surface of the second section of the sliding portion 322, and the oil path is blocked. Since the second port B is communicated with the second hydraulic chamber B ' through the second oil passage on the piston 2, and the third port C is communicated with the third hydraulic chamber C ' through the third oil passage on the piston 2, when the second port B and the third port C in the two-position three-way valve are communicated, the second hydraulic chamber B ' and the third hydraulic chamber C ' in the piston housing are communicated, and the high-pressure liquid flows into the third hydraulic chamber C ' from the second hydraulic chamber B ', so as to form the movement oil passage of the piston 2 shown in fig. 4, the first hydraulic chamber a ' is in a low-pressure state, and the second hydraulic chamber B ' and the third hydraulic chamber C ' are in a high-pressure state, and are pushed by the hydraulic pressure (the hydraulic pressure is F pS pi (D2 is F pi) (p pi) (the hydraulic pressure is F p pi) (D2)2-D32) And/4), the piston moves leftwards (i.e. in the second direction) as a whole.
The hydraulic reciprocating driving mechanism disclosed in the embodiment can realize the reciprocating motion of the piston 2 as long as the hydraulic pressure in the first hydraulic chamber A 'is lower than the hydraulic pressure in the second hydraulic chamber B' due to the special structural design, the reversing of the piston is automatic reversing, no external control is needed, the reversing impact force on the valve core 32 and the piston 2 in the reversing valve is smaller during reversing, the piston 2 runs stably, compared with the traditional three-cylinder single-action piston pump, the hydraulic reciprocating driving mechanism in the embodiment has no rotating part, can realize automatic reversing, has few easily damaged parts, has a simple control mode, is low in running cost, and is compact in structure, small in size and light in weight.
Of course, in other specific embodiments of the hydraulic reciprocating driving mechanism of the invention, the relative position relationship of the three hydraulic chambers can be adjusted according to actual needs, the specific structures of the corresponding piston and the piston shell should be adaptively adjusted accordingly, when the adjustment is carried out, it is only required to ensure that the piston moves in one direction under the action of hydraulic pressure when high-pressure liquid is introduced into the variable hydraulic chamber, and when low-pressure oil is introduced into the variable hydraulic chamber, the piston moves in the opposite direction under the action of hydraulic pressure; in addition, the hydraulic system can directly input high-pressure liquid and low-pressure liquid into the first hydraulic chamber and the second hydraulic chamber, and can also transmit the high-pressure liquid and the low-pressure liquid through a valve or other structures; the reversing valve for controlling the piston to steer can also adopt other control structures besides a two-position three-way valve; the two-position three-way valve can be arranged inside the piston and also can be arranged outside the piston; the specific structure of the two-position three-way valve and the mode of controlling the piston can be adjusted adaptively according to actual needs, and details are not repeated here.
As shown in fig. 7 and 8, the present embodiment discloses a hydraulic reciprocating pump, which includes the above-mentioned hydraulic reciprocating driving mechanism and a pump housing 4, the pump housing 4 is disposed outside the piston housing 1, and a first working chamber 41 and a second working chamber 42 are disposed inside the pump housing 4, the first working chamber 41 and the second working chamber 42 are symmetrically disposed, and the first end of the piston 2, i.e. the first acting portion 21 of the piston, acts on the first working chamber 41, and the second end of the piston 2, i.e. the second acting portion 24 of the piston, acts on the second working chamber 42. Under a first preset working condition, the first working chamber 41 sucks working liquid, and the second working chamber 42 discharges the working liquid; in the second preset condition, the first working chamber 41 discharges the working fluid, and the second working chamber 42 sucks the working fluid.
Specifically, a first check valve 43 and a second check valve are arranged on the first working chamber 41, a third check valve and a fourth check valve are arranged on the second working chamber 42, the first check valve 43 and the second check valve are arranged on different sides of the first working chamber 41, the third check valve and the fourth check valve are respectively arranged on different sides of the second working chamber 42, the first check valve 43 and the third check valve are located on the same side, namely, the lower side shown in fig. 7 and 8, and the second check valve and the fourth check valve are located on the same side, namely, the upper side shown in fig. 7 and 8. Under a first preset working condition, the first check valve 43 is opened, the second check valve is closed, the third check valve is closed, the fourth check valve is opened, the first working chamber 41 sucks working liquid, and the second working chamber 42 discharges the working liquid. Under a second preset working condition, the first check valve 43 is closed, the second check valve is opened, the third check valve is opened, the fourth check valve is closed, the first working chamber 41 discharges working liquid, and the second working chamber 42 sucks in the working liquid.
As shown in fig. 7 and 8, the hydraulic reciprocating pump in this embodiment further includes a housing, a water inlet cavity 51 and a water outlet cavity 52 are disposed in the housing, the first working cavity 41 is communicated with the water inlet cavity 51 through the first check valve 43 and is communicated with the water outlet cavity 52 through the second check valve, and the second working cavity 42 is communicated with the water inlet cavity 51 through the third check valve and is communicated with the water outlet cavity 52 through the fourth check valve.
The hydraulic reciprocating driving mechanism pump disclosed in the embodiment can realize automatic reversing, is simple in control mode, compact in structure, small in size, light in weight, easy for product serialization expansion, can replace the traditional reciprocating pump widely used in various industries and pumps with other structural forms at present, and has a good application prospect.
Of course, in other specific embodiments of the hydraulic reciprocating driving mechanism pump of the present invention, only one working chamber may be provided in the pump casing, and the valve provided on the working chamber may also be a valve of other forms, as long as the working chamber can be switched on and off according to the hydraulic pressure in the working chamber, which is not described herein again.
It should be noted that the above embodiments can be freely combined as necessary. 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 amendments can be made without departing from the principle of the present invention, and these modifications and amendments should also be considered as the protection scope of the present invention.
Claims (10)
1. A hydraulic reciprocating drive mechanism, comprising:
the piston shell is internally provided with a hydraulic chamber;
a piston disposed in a hydraulic chamber of the piston housing and separating the hydraulic chamber into a first hydraulic chamber, a second hydraulic chamber, and a third hydraulic chamber;
a hydraulic system that passes low pressure fluid to the first hydraulic chamber and high pressure fluid to the second hydraulic chamber, the hydraulic system being actuated to:
under a first preset working condition, low-pressure liquid is introduced into the third hydraulic chamber, the first hydraulic chamber is communicated with the third hydraulic chamber, and the high-pressure liquid in the second hydraulic chamber pushes the piston to move towards a first direction;
under a second preset working condition, high-pressure liquid is introduced into the third hydraulic chamber, the second hydraulic chamber is communicated with the third hydraulic chamber, the piston is pushed by the high-pressure liquid in the second hydraulic chamber and the third hydraulic chamber to move towards a second direction, and the second direction is opposite to the first direction.
2. The hydraulic reciprocating drive mechanism of claim 1, wherein:
the first hydraulic chamber, the second hydraulic chamber and the third hydraulic chamber are arranged in sequence, and the second hydraulic chamber is positioned between the first hydraulic chamber and the third hydraulic chamber;
the first direction is a direction in which the first hydraulic chamber is directed to the second hydraulic chamber, and the second direction is a direction in which the second hydraulic chamber is directed to the first hydraulic chamber.
3. The hydraulic reciprocating drive mechanism of claim 2, wherein:
the piston comprises a first acting part, a first driving part, a second driving part and a second acting part which are sequentially arranged, wherein the radial sizes of the first acting part, the first driving part and the second driving part are sequentially increased, and the radial sizes of the first acting part and the second acting part are the same;
the hydraulic chamber of the piston shell is a first section, a second section, a third section, a fourth section and a fifth section which are sequentially arranged, and the radial size of the third section is smaller than that of the second section and the fourth section;
the first driving part is arranged at a third section of the hydraulic chamber in a sealing and sliding manner and separates the second section from the fourth section, and the second section is the first hydraulic chamber;
the second driving part is arranged at the first section of the hydraulic chamber in a sealing and sliding manner and divides the fourth section into the second hydraulic chamber and the third hydraulic chamber;
the first acting part is arranged at the fourth section of the hydraulic chamber in a sealing and sliding manner, and the second acting part is arranged at the fifth section of the hydraulic chamber in a sealing and sliding manner.
4. The hydraulic reciprocating drive mechanism of claim 2, wherein:
the hydraulic system comprises a low-pressure liquid output end and a high-pressure liquid output end, the low-pressure liquid output end is directly communicated with the first hydraulic chamber, and the high-pressure liquid output end is directly communicated with the second hydraulic chamber.
5. The hydraulic reciprocating drive mechanism of claim 4, wherein:
the hydraulic system further comprises a two-position three-way valve, wherein the two-position three-way valve comprises a first oil port communicated with the first hydraulic chamber, a second oil port communicated with the second hydraulic chamber and a third oil port communicated with the third hydraulic chamber;
under the first preset working condition, the first oil port is communicated with the third oil port;
and under the second preset working condition, the second oil port is communicated with the third oil port.
6. The hydraulic reciprocating drive mechanism of claim 5, wherein:
the two-position three-way valve is positioned inside the piston, and a first oil way, a second oil way and a third oil way are arranged on the piston;
one port of the first oil path is communicated with the first hydraulic chamber, and the other port of the first oil path is communicated with the first oil port;
one port of the second oil path is communicated with the second hydraulic chamber, and the other port of the second oil path is communicated with the second oil port;
one port of the third oil passage is communicated with the third hydraulic chamber, and the other port of the third oil passage is communicated with the third oil port.
7. The hydraulic reciprocating drive mechanism of claim 6, wherein:
the two-position three-way valve comprises a valve shell and a valve core;
the valve element comprises a fixed part and a sliding part, wherein the sliding part comprises a first section, a second section, a third section and a fourth section which are sequentially arranged along the first direction, the outer diameters of the first section, the second section and the third section of the sliding part are gradually reduced, the outer diameter of the second section of the sliding part is equal to that of the fourth section of the sliding part, a stepped through hole is arranged in the sliding part, the aperture of the first section of the stepped through hole is larger than that of the second section of the stepped through hole, and the stepped through hole is arranged outside the fixed part in a sealing and sliding manner along the first section of the through hole in the first direction;
the inner cavity of the valve casing comprises a first section and a second section which are sequentially arranged along the first direction, the radial size of the first section of the valve casing is larger than that of the second section of the valve casing, the first section and the second section of the valve casing are positioned on two sides of the first oil port, and the second oil port and the third oil port are arranged at the second section of the valve casing;
the first section of the sliding part is hermetically and slidably arranged on the first section of the valve shell, and the second section and the fourth section of the sliding part are hermetically and slidably arranged on the second section of the valve shell;
a fourth oil path is arranged on the piston, a fourth oil port is arranged on the second section of the valve shell, one port of the fourth oil path is communicated with the second hydraulic chamber, the other port of the fourth oil path is communicated with the fourth oil port, and the fourth oil path is always communicated with an inner cavity of the valve shell positioned on one side of the valve core;
a fifth oil passage is arranged on the piston, a fifth oil port is arranged on the first section of the valve shell, and one port of the fifth oil passage is communicated with the fifth oil port;
when the other end of the fifth oil path is communicated with the first hydraulic chamber, the sliding part moves along the second direction, and the first oil port is communicated with the third oil port;
when the other end of the fifth oil passage is communicated with the second hydraulic chamber, the sliding part moves along the first direction, and the second oil port is communicated with the third oil port.
8. A hydraulic reciprocating pump, comprising:
the hydraulic reciprocating drive mechanism of any one of claims 1 to 7;
the pump shell is arranged outside the piston shell, a first working cavity is arranged in the pump shell, and the first end of the piston acts on the first working cavity;
under the first preset working condition, the first working cavity sucks working liquid;
and under the second preset working condition, the first working chamber discharges working liquid.
9. The hydraulic reciprocating pump of claim 8, wherein:
the first working cavity is provided with a first one-way valve and a second one-way valve, and the first one-way valve and the second one-way valve are arranged on different sides of the first working cavity;
under the first preset working condition, the first one-way valve is opened, and the second one-way valve is closed;
and under the second preset working condition, the first one-way valve is closed, and the second one-way valve is opened.
10. The hydraulic reciprocating pump of claim 9, wherein:
a second working cavity is further arranged in the pump shell, the second working cavity and the first working cavity are symmetrically arranged, and the second end of the piston acts on the second working cavity;
under the first preset working condition, the second working chamber discharges working liquid;
under the second preset working condition, the second working cavity sucks working liquid;
a third one-way valve and a fourth one-way valve are arranged on the second working cavity, the third one-way valve and the fourth one-way valve are respectively arranged on different sides of the second working cavity, the third one-way valve and the first one-way valve are positioned on the same side, and the fourth one-way valve and the second one-way valve are positioned on the same side;
under the first preset working condition, the third one-way valve is closed, and the fourth one-way valve is opened;
and under the second preset working condition, the third one-way valve is opened, and the fourth one-way valve is closed.
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| CN201711170432.7A CN108167261B (en) | 2017-11-22 | 2017-11-22 | Hydraulic reciprocating driving mechanism and hydraulic reciprocating driving pump |
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| CN201711170432.7A CN108167261B (en) | 2017-11-22 | 2017-11-22 | Hydraulic reciprocating driving mechanism and hydraulic reciprocating driving pump |
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| CN108167261B true CN108167261B (en) | 2022-07-12 |
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| CN1440489A (en) * | 2000-05-19 | 2003-09-03 | 博世力士乐股份有限公司 | Free piston motor |
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| JP4148425B1 (en) * | 2007-03-12 | 2008-09-10 | 光治 馬上 | High pressure generator |
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| US8061179B2 (en) * | 2008-08-12 | 2011-11-22 | GM Global Technology Operations LLC | High pressure dual-action hydraulic pump |
| US10161396B2 (en) * | 2015-09-17 | 2018-12-25 | Monkey Pumps, LLC | Zero emission reciprocating drive pump |
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| CN1440489A (en) * | 2000-05-19 | 2003-09-03 | 博世力士乐股份有限公司 | Free piston motor |
| CN101892942A (en) * | 2010-06-01 | 2010-11-24 | 浙江大学 | Single piston hydraulic free-piston engine capable of reducing pumping flow pulsation |
| CN104929766A (en) * | 2014-03-21 | 2015-09-23 | 北京理工大学 | Hydraulic free piston engine |
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