CN113446280B - Bidirectional differential pressure controller and hydraulic equipment - Google Patents
Bidirectional differential pressure controller and hydraulic equipment Download PDFInfo
- Publication number
- CN113446280B CN113446280B CN202110740366.2A CN202110740366A CN113446280B CN 113446280 B CN113446280 B CN 113446280B CN 202110740366 A CN202110740366 A CN 202110740366A CN 113446280 B CN113446280 B CN 113446280B
- Authority
- CN
- China
- Prior art keywords
- valve body
- sliding part
- limit joint
- pore canal
- cavity
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000002457 bidirectional effect Effects 0.000 title claims abstract description 45
- 230000007246 mechanism Effects 0.000 claims abstract description 9
- 239000011148 porous material Substances 0.000 claims description 49
- 230000009471 action Effects 0.000 claims description 10
- 230000008602 contraction Effects 0.000 claims description 3
- 230000008859 change Effects 0.000 abstract description 8
- 239000003921 oil Substances 0.000 description 31
- 238000000034 method Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 206010063385 Intellectualisation Diseases 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000010729 system oil Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/028—Shuttle valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/04—Construction of housing; Use of materials therefor of sliding valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Reciprocating Pumps (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a bidirectional differential pressure controller, which comprises: the valve body and the shell are both provided with a hollow cavity, the valve body is positioned in the hollow cavity of the shell, the valve core is positioned in the hollow cavity of the valve body, the first limit joint and the second limit joint are respectively positioned at two ends of the shell, one end of the first sliding part is fixedly connected with the first limit joint, the other end of the first sliding part is fixedly connected with one end of the valve core, the other end of the valve core is fixedly connected with one end of the second sliding part, and the other end of the second sliding part is fixedly connected with one end of the second limit joint. The invention can solve the problem that when the rotation direction of the bidirectional variable hydraulic pump or the hydraulic motor is changed, namely when the inlet and the outlet of the hydraulic pump or the hydraulic motor are changed, the high-pressure outlet of the hydraulic pump or the high-pressure inlet of the hydraulic motor is always communicated with the hydraulic cavity of the swash plate variable mechanism, the high-pressure change is induced, the angle of the swash plate is automatically adjusted, and the hydraulic pump or the hydraulic motor can be controlled in a servo mode according to the load change.
Description
Technical Field
The invention relates to the technical field of hydraulic systems, in particular to a bidirectional differential pressure controller and hydraulic equipment.
Background
The hydraulic pump and the hydraulic motor are core components of a hydraulic system, the hydraulic pump which is commonly used at present is a unidirectional variable hydraulic pump or a bidirectional quantitative hydraulic pump, the hydraulic motor is a bidirectional quantitative hydraulic motor, and along with the development of industrial automation and intellectualization, the servo control is used as a trend to provide the functional requirements of bidirectional variables for the hydraulic pump and the hydraulic motor.
Whether it is a two-way variable hydraulic pump or a two-way variable hydraulic motor, if the swash plate is held at an angle, two-way means that the inner shaft needs to rotate in both forward and reverse directions, and the direction of the inlet and outlet oil can be changed, i.e. the inlet and outlet of the hydraulic pump or the hydraulic motor are interchanged. The variable requires that the hydraulic pump or the hydraulic motor can track the angle of the swash plate in both the left and right directions under the condition of load change so as to make proper adjustment, so that the angle of the swash plate is in dynamic change and is kept at a proper value. Therefore, when the rotation direction is changed and the inlet and outlet are changed, namely the high-pressure port and the low-pressure port are exchanged, the high-pressure port is still required to be always communicated with the hydraulic cavity of the swash plate variable mechanism.
Disclosure of Invention
To solve at least one of the above technical problems, the present disclosure provides a bidirectional differential pressure controller and a hydraulic apparatus.
In a first aspect, an embodiment of the present invention provides a bidirectional differential pressure controller, including: the valve comprises a first limit joint, a first sliding part, a valve core, a second sliding part, a second limit joint, a valve body and a shell; the valve body and the shell are provided with hollow cavities, the valve body is positioned in the hollow cavity of the shell, the valve core is positioned in the hollow cavity of the valve body, a first limit joint and a second limit joint are respectively positioned at two ends of the shell, one end of the first sliding part is fixedly connected with the first limit joint, the other end of the first sliding part is fixedly connected with one end of the valve core, the other end of the valve core is fixedly connected with one end of the second sliding part, and the other end of the second sliding part is fixedly connected with one end of the second limit joint;
The first limit joint and the second limit joint are respectively fixed at two ends of the shell and can be respectively connected with an inlet oil way and an outlet oil way of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor through the first limit joint and the second limit joint so as to realize bidirectional differential pressure control of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor; the valve core is sleeved in the valve body and can slide in the valve body under the action of the first sliding part and the second sliding part; the first sliding part and the second sliding part can be reset springs, and the valve core can relatively move under the action of extension and contraction of the reset springs; after the first limit joint and the second limit joint are connected with an inlet oil way and an outlet oil way of the two-way variable hydraulic pump or the two-way variable hydraulic motor, oil enters a hollow cavity of the valve body through a first pore canal at one side of the first limit joint, the first closed cavity is communicated with the hollow cavity of the valve body, and then the oil enters the first closed cavity;
The valve body is provided with a third pore canal, the third pore canal penetrates through the outer surface and the inner surface of the valve body, the shell is provided with a fourth pore canal, the fourth pore canal penetrates through the outer surface and the inner surface of the shell, and the third pore canal is communicated with the fourth pore canal.
Optionally, the first spacing joint is provided with first pore with the cavity intercommunication of valve body one end, the second spacing joint is provided with the second pore with the cavity intercommunication of the valve body other end, the surface of case with form first closed chamber and second closed chamber between the internal surface of valve body, first closed chamber with the second closed chamber is not mutually communicated, first closed chamber with the cavity intercommunication of valve body one end, the second closed chamber with the cavity intercommunication of valve body other end.
Optionally, the valve body is further provided with a fifth duct and a sixth duct, both penetrating through the outer surface and the inner surface of the valve body, and the third duct being located between the fifth duct and the sixth duct.
Optionally, the first closed cavity is located between the third duct and the fifth duct, and the length of the first closed cavity is smaller than or equal to the interval between the third duct and the fifth duct; the second closed cavity is positioned between the third pore canal and the sixth pore canal, and the length of the second closed cavity is smaller than or equal to the interval between the third pore canal and the sixth pore canal.
Optionally, the fifth orifice communicates with the sixth orifice.
Optionally, the first sliding portion and the second sliding portion are both return springs.
In a second aspect, the present invention provides a hydraulic apparatus comprising the bi-directional pressure differential controller of the first aspect, the hydraulic apparatus comprising a hydraulic pump or a hydraulic motor.
Optionally, the first limit joint and the second limit joint of the bidirectional differential pressure controller are respectively connected with an inlet oil way and an outlet oil way of the hydraulic equipment, and the fourth pore canal of the bidirectional differential pressure controller is connected with a swash plate variable mechanism hydraulic cavity of the hydraulic equipment.
Compared with the prior art, the invention has at least the following beneficial effects:
The invention can solve the problem that when the rotation direction of the bidirectional variable hydraulic pump or the hydraulic motor is changed, namely when the inlet and the outlet of the hydraulic pump or the hydraulic motor are changed, the high-pressure outlet of the hydraulic pump or the high-pressure inlet of the hydraulic motor is always communicated with the hydraulic cavity of the swash plate variable mechanism, the high-pressure change is induced, the angle of the swash plate is automatically adjusted, and the hydraulic pump or the hydraulic motor can be controlled in a servo mode according to the load change.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a bi-directional differential pressure controller according to an embodiment of the present invention;
FIG. 2 is a schematic diagram showing the relative positions of the valve element of the valve body when the valve element moves L1 according to one embodiment of the present invention;
FIG. 3 is a schematic diagram showing the relative positions of the valve cores of the valve body when the valve cores are moved L2 according to one embodiment of the invention;
FIG. 4 is a schematic diagram showing the relative positions of the valve cores of the valve body when the valve cores are not moved according to one embodiment of the invention.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments, and all other embodiments obtained by those skilled in the art without making any inventive effort based on the embodiments of the present invention are within the scope of protection of the present invention.
As shown in fig. 1, an embodiment of the present invention provides a bidirectional differential pressure controller, including: the valve comprises a first limit joint 1, a first sliding part 2, a valve core 3, a second sliding part 4, a second limit joint 5, a valve body 6 and a shell 7; the valve body 6 and the shell 7 are respectively provided with a hollow cavity, the valve body 6 is located in the hollow cavity of the shell 7, the valve core 3 is located in the hollow cavity of the valve body 6, the first limit joint 1 and the second limit joint 5 are respectively located at two ends of the shell 7, one end of the first sliding part 2 is fixedly connected with the first limit joint 1, the other end of the first sliding part 2 is fixedly connected with one end of the valve core 3, the other end of the valve core 3 is fixedly connected with one end of the second sliding part 4, and the other end of the second sliding part 4 is fixedly connected with one end of the second limit joint 5. The first limiting joint 1 is provided with a first pore canal 11 and is communicated with a hollow cavity 61 at one end of the valve body 6, the second limiting joint 5 is provided with a second pore canal 51 and is communicated with the hollow cavity 61 at the other end of the valve body 6, a first closed cavity 31 and a second closed cavity 32 are formed between the outer surface of the valve core 3 and the inner surface of the valve body 6, the first closed cavity 31 and the second closed cavity 32 are not communicated with each other, the first closed cavity 31 and the hollow cavity 61 at one end of the valve body are communicated, and the second closed cavity 32 and the hollow cavity 61 at the other end of the valve body are communicated.
It should be noted that, the first limiting connector 1 and the second limiting connector 5 are respectively fixed at two ends of the casing 7, and the first limiting connector 1 and the second limiting connector 5 can be respectively connected with an inlet oil circuit and an outlet oil circuit of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor so as to realize bidirectional differential pressure control of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor. The valve core 3 is sleeved in the valve body 6, and the valve core 3 can slide in the valve body 6 under the action of the first sliding part 2 and the second sliding part 4. The first sliding portion 2 and the second sliding portion 4 may be return springs, and the valve element 3 is relatively moved by the expansion and contraction and the extension of the return springs. After the first limit joint 1 and the second limit joint 5 are connected with the inlet oil path and the outlet oil path of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor, oil enters the hollow cavity 61 of the valve body 6 through the first pore canal 11 at the side of the first limit joint 1, the first closed cavity 31 is communicated with the hollow cavity 61 of the valve body, and then the oil enters the first closed cavity 31, and similarly, at the side of the second limit joint 5, the oil enters the hollow cavity 61 of the valve body 6 through the second pore canal 51, and the second closed cavity 32 is communicated with the hollow cavity 61 of the valve body, and then the oil enters the second closed cavity 32.
As shown in fig. 1, in the embodiment of the present invention, a third hole 62 is disposed on the valve body 6, the third hole 62 penetrates through the outer surface and the inner surface of the valve body 6, a fourth hole 71 is disposed on the housing 7, the fourth hole 71 penetrates through the outer surface and the inner surface of the housing 7, and the third hole 62 communicates with the fourth hole 71. The valve body 6 is further provided with a fifth port 63 and a sixth port 64, the fifth port 63 and the sixth port 64 penetrate through the outer surface and the inner surface of the valve body 6, and the third port 62 is located between the fifth port 63 and the sixth port 64.
It should be noted that, when the valve element 3 does not move relatively in the valve body 6, the first closed chamber 31 does not communicate with any of the third port 62, the fifth port 63 and the sixth port 64, and likewise, the second closed chamber 32 does not communicate with any of the third port 62, the fifth port 63 and the sixth port 64. When the valve core 3 moves relatively in the valve body 6, if the valve core moves to one side of the first limit joint 1, the first closed cavity 31 is communicated with the fifth pore passage 63, and meanwhile, the second closed cavity 32 is communicated with the third pore passage 62; in another example, moving to one side of the second spacing tab 5, the first closed cavity 31 will be in communication with the third aperture 62, while the second closed cavity 32 will be in communication with the sixth aperture 64. Thus, the first closed cavity 31 is located between the third and fifth cells 62, 63, and the length of the first closed cavity 31 is equal to or less than the spacing between the third and fifth cells 62, 63; the second closed cavity 32 is located between the third orifice 62 and the sixth orifice 64, and the length of the second closed cavity 32 is less than or equal to the distance between the third orifice 62 and the sixth orifice 64.
The following describes a procedure in which a bidirectional differential pressure controller is applied to a hydraulic device for servo control in two rotational directions according to a load change. The hydraulic device comprises a hydraulic pump or a hydraulic motor. The first limit joint and the second limit joint of the bidirectional differential pressure controller are respectively connected with an inlet oil way and an outlet oil way of the hydraulic equipment, and a fourth pore canal of the bidirectional differential pressure controller is communicated with a swash plate variable mechanism hydraulic cavity of the hydraulic equipment.
As shown in fig. 1-4, when high-pressure oil enters from the port a and low-pressure oil enters from the port B, the two-way variable hydraulic pump is used, the corresponding first limit joint 1 is connected to the outlet, the second limit joint 5 is connected to the inlet, and when the two-way variable hydraulic motor is used, the corresponding first limit joint 1 is connected to the inlet, the second limit joint 5 is connected to the outlet, at this time, the high-pressure oil enters the left end closed cavity 31 of the valve core 3 through the first through hole 11 of the first limit joint 1, that is, kong a, through the left return spring 2, and simultaneously, the low-pressure oil enters the right end closed cavity 32 of the valve core 3 through the second hole 51 of the second limit joint 5, that is, kong B, through the right return spring 4, and because the high-pressure on the left side and the low-pressure on the right side form a rightward differential pressure, the differential acts on the valve core 3, so that the valve core 3 receives a rightward hydraulic force Fy, the left side return spring 2 gives a rightward elastic force Ft1 to the valve core 3, and the right side return spring 4 gives a leftward elastic force Ft2, 3, and the left side stress relation is as follows: fy+Ft1> Ft2, so that the valve core 3 moves rightwards under the action of force, when the valve core moves L1 distance (see figure 2), high-pressure oil is communicated with the third pore passage 62 on the valve body 6, enters a hydraulic cavity of a swash plate variable mechanism of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor through the third pore passage 62 and the fourth pore passage 71 on the shell 7, and low-pressure oil is communicated with the fifth pore passage 63 and the sixth pore passage 64 on the valve body 6 and enters the port B.
When the low pressure oil enters from the port A and the high pressure oil enters from the port B, when the hydraulic pump is used for a bidirectional variable hydraulic pump, the inlet is connected with the corresponding first limit joint 1, the outlet is connected with the corresponding second limit joint 5, when the hydraulic pump is used for a bidirectional variable hydraulic motor, the outlet is connected with the corresponding first limit joint 1, the inlet is connected with the corresponding second limit joint 5, at this time, the high pressure oil passes through the second pore canal 51 of the second limit joint 5, the return spring 4 on the right side enters into the right end closed cavity 32 of the valve core 3, meanwhile, the low pressure oil passes through the first pore canal 11 of the first limit joint 1, the return spring 2 on the left side enters into the left end closed cavity 31 of the valve core 3, and as the high pressure on the right side and the low pressure on the left side form a leftward pressure difference, the pressure difference acts on the valve core 3, so that the valve core 3 is subjected to a leftward hydraulic pressure force Fy, the return spring on the valve core 3, and the left side return spring 4 gives an elastic force Ft1 to the valve core 3 to the leftward, and the return spring 2 on the valve core 3 to the right side: fy+Ft1> Ft2, so that the valve core 3 moves leftwards under the action of force, when the valve core moves L2 distance (see figure 3), high-pressure oil is communicated with the third pore passage 62 on the valve body 6, enters a swash plate variable mechanism hydraulic cavity of the two-way variable hydraulic pump or the two-way variable hydraulic motor through the third pore passage 62 on the valve body 6 and the fourth pore passage 71 on the shell 7, and is communicated with the fifth pore passage 63 and the sixth pore passage 64 on the valve body 6 to enter an opening A.
When the inlet A and the inlet B are all low-pressure oil, namely, the two-way variable hydraulic pump or the hydraulic motor used is in an unoperated state, the connected hydraulic pressure is the system oil tank pressure, the hydraulic pressures born by the left side and the right side of the valve core 3 are equal and opposite, and meanwhile, the elastic force of the return spring 2 and the return spring 4 on the left side and the right side to the valve core 3 is equal and opposite, so that the resultant force of the hydraulic pressure and the elastic force born by the left side and the right side of the valve core 3 is zero and always kept at the middle position (see figure 4), at the moment, the third pore channel, the fifth pore channel and the sixth pore channel on the valve body 3 are not communicated with the inlet A or the outlet B, and the inlet A and the outlet B are kept relatively independent.
The bidirectional differential pressure controller provided by the invention can realize the left-right rotation conversion of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor, namely, when the port A and the port B are switched between high pressure and low pressure, the high pressure side is always ensured to be communicated with the third port, and the hydraulic pressure enters the hydraulic cavity of the swash plate variable mechanism of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor through the third port, so that the swash plate can adjust the inclination angle of the swash plate through sensing high pressure, and the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor can carry out servo control according to load change in two rotation directions.
It is noted that relational terms such as first and second, and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the statement "comprises one" does not exclude that an additional identical element is present in a process, method, article or apparatus that comprises the element.
Finally, it should be noted that: the foregoing description is only illustrative of the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention are included in the protection scope of the present invention.
Claims (8)
1. A bi-directional pressure differential controller, comprising: the valve comprises a first limit joint, a first sliding part, a valve core, a second sliding part, a second limit joint, a valve body and a shell; the valve body and the shell are provided with hollow cavities, the valve body is positioned in the hollow cavity of the shell, the valve core is positioned in the hollow cavity of the valve body, a first limit joint and a second limit joint are respectively positioned at two ends of the shell, one end of the first sliding part is fixedly connected with the first limit joint, the other end of the first sliding part is fixedly connected with one end of the valve core, the other end of the valve core is fixedly connected with one end of the second sliding part, and the other end of the second sliding part is fixedly connected with one end of the second limit joint;
The first limit joint and the second limit joint are respectively fixed at two ends of the shell and can be respectively connected with an inlet oil way and an outlet oil way of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor through the first limit joint and the second limit joint so as to realize bidirectional differential pressure control of the bidirectional variable hydraulic pump or the bidirectional variable hydraulic motor; the valve core is sleeved in the valve body and can slide in the valve body under the action of the first sliding part and the second sliding part; the first sliding part and the second sliding part can be reset springs, and the valve core can relatively move under the action of extension and contraction of the reset springs; after the first limit joint and the second limit joint are connected with an inlet oil way and an outlet oil way of the two-way variable hydraulic pump or the two-way variable hydraulic motor, oil enters a hollow cavity of the valve body through a first pore canal at one side of the first limit joint, the first closed cavity is communicated with the hollow cavity of the valve body, and then the oil enters the first closed cavity;
The valve body is provided with a third pore canal, the third pore canal penetrates through the outer surface and the inner surface of the valve body, the shell is provided with a fourth pore canal, the fourth pore canal penetrates through the outer surface and the inner surface of the shell, and the third pore canal is communicated with the fourth pore canal.
2. The bi-directional pressure differential controller of claim 1, wherein the first limiting joint is provided with a first pore canal and is communicated with a hollow cavity at one end of the valve body, the second limiting joint is provided with a second pore canal and is communicated with a hollow cavity at the other end of the valve body, a first closed cavity and a second closed cavity are formed between the outer surface of the valve core and the inner surface of the valve body, the first closed cavity is not communicated with the second closed cavity, the first closed cavity is communicated with the hollow cavity at one end of the valve body, and the second closed cavity is communicated with the hollow cavity at the other end of the valve body.
3. The bi-directional pressure differential controller of claim 1, wherein the valve body is further provided with a fifth orifice and a sixth orifice, both of which extend through the outer and inner surfaces of the valve body, the third orifice being located between the fifth orifice and the sixth orifice.
4. The bi-directional pressure differential controller of claim 3, wherein the first closed chamber is located between the third orifice and the fifth orifice, the first closed chamber having a length that is less than or equal to a spacing between the third orifice and the fifth orifice; the second closed cavity is positioned between the third pore canal and the sixth pore canal, and the length of the second closed cavity is smaller than or equal to the interval between the third pore canal and the sixth pore canal.
5. A bi-directional pressure differential controller as defined in claim 3, wherein said fifth port communicates with said sixth port.
6. The bi-directional pressure differential controller as recited in any of claims 1-5, wherein said first sliding portion and said second sliding portion are both return springs.
7. A hydraulic apparatus comprising the bi-directional pressure differential controller of any one of claims 1-6, the hydraulic apparatus comprising a hydraulic pump or a hydraulic motor.
8. The hydraulic apparatus of claim 7, wherein the first and second limit joints of the bi-directional pressure differential controller are connected to an inlet oil passage and an outlet oil passage of the hydraulic apparatus, respectively, and the fourth port of the bi-directional pressure differential controller is connected to a swash plate variable mechanism hydraulic chamber of the hydraulic apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110740366.2A CN113446280B (en) | 2021-06-30 | 2021-06-30 | Bidirectional differential pressure controller and hydraulic equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110740366.2A CN113446280B (en) | 2021-06-30 | 2021-06-30 | Bidirectional differential pressure controller and hydraulic equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113446280A CN113446280A (en) | 2021-09-28 |
| CN113446280B true CN113446280B (en) | 2024-06-25 |
Family
ID=77814519
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110740366.2A Active CN113446280B (en) | 2021-06-30 | 2021-06-30 | Bidirectional differential pressure controller and hydraulic equipment |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113446280B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AR243659A1 (en) * | 1982-08-05 | 1993-08-31 | Deere & Co | Proportional hydraulic valve for precision control |
| CN109469594A (en) * | 2018-09-29 | 2019-03-15 | 北京航空航天大学 | Continuously Regulating Electro-hydraulic Proportional Axial Piston Variable Pump for Aircraft Hydraulic System |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1162976A (en) * | 1965-09-22 | 1969-09-04 | English Electric Co Ltd | Improvements in or relating to Hydraulic Reciprocating Pumps and Motors |
| JP2560640Y2 (en) * | 1993-01-25 | 1998-01-26 | 株式会社トキメック | Pilot operated solenoid proportional valve |
| KR100474258B1 (en) * | 1997-05-31 | 2005-05-24 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | Swash Plate Type Axial Piston Pump |
| JPH1122646A (en) * | 1997-07-04 | 1999-01-26 | Nisso Eng Kk | Fluid pressure drive pump |
| JPH11210634A (en) * | 1998-01-30 | 1999-08-03 | Hitachi Constr Mach Co Ltd | Capacity control device of liquid pressure rotary machine |
| KR20130065996A (en) * | 2011-12-12 | 2013-06-20 | 현대중공업 주식회사 | Valve plate |
| CN205349895U (en) * | 2015-12-28 | 2016-06-29 | 广东科达洁能股份有限公司 | Control valve, variable axial plunger pump and hydraulic system |
| CN111677623B (en) * | 2020-06-19 | 2022-04-22 | 中航力源液压股份有限公司 | Control valve device with override control for pressure difference between inlet and outlet of induction motor |
| CN112302895A (en) * | 2020-11-25 | 2021-02-02 | 力源液压（苏州）有限公司 | Axial plunger pump |
| CN112377381A (en) * | 2020-11-25 | 2021-02-19 | 力源液压（苏州）有限公司 | Electric proportional plunger pump and variable control device thereof |
| CN112576781B (en) * | 2020-12-23 | 2024-05-31 | 涌镇液压机械（上海）有限公司 | Proportional valve with decompression and reversing functions |
| CN112879372A (en) * | 2021-03-15 | 2021-06-01 | 力源液压（苏州）有限公司 | Pressure regulating valve of bidirectional variable plunger pump |
-
2021
- 2021-06-30 CN CN202110740366.2A patent/CN113446280B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AR243659A1 (en) * | 1982-08-05 | 1993-08-31 | Deere & Co | Proportional hydraulic valve for precision control |
| CN109469594A (en) * | 2018-09-29 | 2019-03-15 | 北京航空航天大学 | Continuously Regulating Electro-hydraulic Proportional Axial Piston Variable Pump for Aircraft Hydraulic System |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113446280A (en) | 2021-09-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4585206A (en) | Proportional flow control valve | |
| KR101296864B1 (en) | Orifice with incorporated filter, slow return valve and hydraulic driving unit | |
| JPS59131073A (en) | Four-way valve with internal pilot | |
| EP0133330B1 (en) | Hydraulic control system | |
| CN113446280B (en) | Bidirectional differential pressure controller and hydraulic equipment | |
| US3693501A (en) | Servo-systems | |
| US3028880A (en) | Fluid flow control valve | |
| US3893484A (en) | Cylinder and piston valve | |
| JPS5822858A (en) | Differential pressure automatic changeover type three-way valve | |
| JPS63210448A (en) | Pilot valve enclosing type actuator | |
| CZ103096A3 (en) | Hydraulic rack device | |
| US4220074A (en) | Switching valve | |
| US3799202A (en) | Power transmission | |
| US3587617A (en) | Fluid control apparatus | |
| CN112324719A (en) | Redundancy electro-hydrostatic actuating system and control method | |
| US20210048111A1 (en) | Fluid valve | |
| EP0001704A1 (en) | Improvements in or relating to valve assemblies and power assisted steering systems | |
| JPS5943679B2 (en) | saatsukanchiben | |
| AU537056B2 (en) | Duplex cam-operated pressure-balanced sleeve valve | |
| US3183785A (en) | Adaptive gain servo actuator | |
| US4191202A (en) | Polarity control valve | |
| LeQuoc et al. | Investigation of an electrohydraulic servovalve with tuneable return pressure and drain orifice | |
| JP2581853Y2 (en) | Pressure compensation valve | |
| CN219994456U (en) | Valve core positioning and resetting device | |
| US2628629A (en) | Flow equalizer valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |