CN111765132B - Pilot-related variable differential pressure compensation system - Google Patents
Pilot-related variable differential pressure compensation system Download PDFInfo
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- CN111765132B CN111765132B CN202010606851.6A CN202010606851A CN111765132B CN 111765132 B CN111765132 B CN 111765132B CN 202010606851 A CN202010606851 A CN 202010606851A CN 111765132 B CN111765132 B CN 111765132B
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- 230000001105 regulatory effect Effects 0.000 claims abstract description 45
- 238000013016 damping Methods 0.000 claims description 27
- 238000005265 energy consumption Methods 0.000 abstract description 7
- 230000009471 action Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 109
- 238000006073 displacement reaction Methods 0.000 description 7
- 230000006872 improvement Effects 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000002596 correlated effect Effects 0.000 description 4
- 239000010720 hydraulic oil Substances 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A pilot-related variable differential pressure compensation system. The problem that the energy consumption is high when the existing quantitative pump control system is low and the large-flow output is difficult to meet when the existing quantitative pump control system works is solved. The hydraulic control system comprises a pressure compensator, a first throttling port, a flow regulating device, a first working oil source and a second working oil source, wherein the flow regulating device is provided with a first closed state and a second open state, when the flow device is in the second state, the first working oil source is connected with a pressure compensator spring cavity after passing through the flow regulating device, and the elastic force of the pressure compensator spring cavity and the pressure oil entering the pressure compensator spring cavity from an oil outlet of the flow regulating device are matched with the first working oil source in a pressure compensator control cavity to control the opening of a valve core of the pressure compensator. The invention also has the advantages of simple structure, reliable action, long service life and the like.
Description
Technical Field
The invention relates to a constant displacement pump control system, in particular to a pilot-related variable differential pressure compensation system.
Background
With the increasing requirements on emissions and energy consumption, it is desirable that the engineering machinery has lower and lower standby fuel consumption, and that the lower and better additional pressure loss during operation is, so that unnecessary fuel consumption can be reduced, and heat generation is reduced.
Although variable displacement pumps are widely applied to engineering machinery, quantitative pump and gear pump systems still have wide application markets by virtue of the characteristics of low cost and simple system, particularly a quantitative pump load sensitive system, and on the one hand, the variable displacement pump has the characteristics of low cost and simple system, and on the other hand, the variable displacement pump has good operability, and is active in the engineering machinery market for a long time.
Typical representatives of the constant displacement pumps are gear pumps, and the load-sensitive system of the gear pump requires a three-way pressure compensator to release the output flow of the gear pump at a lower pressure when the working mechanism is not acting; when the working mechanism acts, the pressure difference between the front and the rear of the throttling groove of the working mechanism can be kept basically constant, and better operability is further provided. In general, the three-way pressure compensator consists of a valve core and a spring, and the spring is an object which is difficult to adjust and change once installed, so that the three-way pressure compensator releases the oil output by the constant delivery pump under a fixed pressure, and the three-way pressure compensator can achieve the following states by changing the state: when the working mechanism does not act, the oil liquid of the constant delivery pump is released under extremely low pressure, and the pressure of the three-way pressure compensator is properly increased along with the increase of the displacement of the valve core of the control working mechanism so as to meet the requirement of the working mechanism for controlling the flow output of the valve core.
Disclosure of Invention
The invention provides a pilot-related variable differential pressure compensation system, which aims to solve the problems that the existing constant displacement pump control system in the background art is high in energy consumption when in low pressure and is difficult to meet high-flow output when in operation.
The technical scheme of the invention is as follows: the pilot-related variable differential pressure compensation system comprises a pressure compensator, a first throttling orifice, a flow regulating device, an oil pump and an oil tank, wherein the oil pump is connected with the oil tank and outputs a first working oil source, the first working oil source outputs a second working oil source after passing through the first throttling orifice, the second working oil source is respectively connected with an executing element and a pressure compensator spring cavity, the flow regulating device is provided with a closed first state and an open second state, and when the flow device is in the first state, the elasticity of the pressure compensator spring cavity, the second working oil source entering the pressure compensator spring cavity and the first working oil source in a pressure compensator control cavity are mutually matched to control the opening of a pressure compensator valve core; when the flow device is in the second state, the first working oil source is connected with the pressure compensator spring cavity after passing through the flow regulating device, and the elastic force of the pressure compensator spring cavity and the pressure oil entering the pressure compensator spring cavity from the oil outlet of the flow regulating device are matched with the first working oil source in the pressure compensator control cavity to control the opening of the valve core of the pressure compensator.
As an improvement of the invention, the device comprises a control device which is respectively connected with the first throttling orifice and the flow regulating device and is respectively used for regulating the flow passing through the first throttling orifice and the flow regulating device.
As a further improvement of the invention, the control source of the control device is a pilot oil source and regulates the flow passing through the first throttling orifice and the flow regulating device through the pressure of the pilot oil source, and the opening pressure of the first throttling orifice is smaller than the opening pressure of the flow regulating device.
As a further improvement of the invention, the hydraulic oil system comprises a constant flow valve, wherein the second working oil source, the spring cavity of the pressure compensator and the oil outlet of the flow regulating device are connected with the oil tank through the constant flow valve.
As a further development of the invention, the second working oil source is connected to the pressure compensator spring chamber via a first non-return valve, a first damping.
As a further improvement of the invention, the flow regulating device comprises a second throttling orifice, a flow valve and a second damping, wherein the first working oil source is connected with the spring cavity of the pressure compensator after passing through the second throttling orifice, the flow valve and the second damping in sequence, the first working oil is connected with the control cavity of the flow valve, the pressure oil at the oil outlet of the second throttling orifice is connected with the spring cavity of the flow valve, the elastic force of the spring cavity of the flow valve, the pressure oil at the oil outlet of the second throttling orifice flowing into the spring cavity of the flow valve and the first working oil flowing into the control cavity of the flow valve are mutually matched to control the opening of the flow valve, and the control device is connected with the second throttling orifice and is used for regulating the flow passing through the second throttling orifice.
As a further improvement of the invention, the flow regulating device comprises a second throttling orifice, a flow valve and a second damping, wherein the first working oil source is connected with the spring cavity of the pressure compensator after passing through the second throttling orifice, the flow valve and the second damping in sequence, the first working oil is connected with the control cavity of the flow valve, the pressure oil of the oil outlet of the second throttling orifice is connected with the spring cavity of the flow valve, and the control device is connected with the spring cavity of the flow valve and is matched with the elasticity of the spring cavity of the flow valve, the pressure oil flowing into the oil outlet of the second throttling orifice of the spring cavity of the flow valve and the first working oil flowing into the control cavity of the flow valve to control the opening of the flow valve.
As a further improvement of the invention, the flow regulating device comprises a second throttling orifice, a flow valve and a second damping, wherein the first working oil source is connected with the spring cavity of the pressure compensator after passing through the second throttling orifice, the flow valve and the second damping in sequence, the first working oil is connected with the control cavity of the flow valve, the pressure oil at the oil outlet of the second throttling orifice is connected with the spring cavity of the flow valve, the elastic force of the spring cavity of the flow valve, the pressure oil at the oil outlet of the second throttling orifice flowing into the spring cavity of the flow valve and the first working oil flowing into the control cavity of the flow valve are mutually matched to control the opening of the flow valve, and the control device is connected with the second damping and is used for regulating the flow passing through the second damping.
As a further improvement of the invention, a second one-way valve is arranged between the flow valve and the second damping.
The invention has the beneficial effects that through the arrangement of the flow regulating device, the pressure compensator releases the oil of the constant delivery pump at extremely low pressure during standby, so that the energy consumption of the product is low, and when large-flow output is required, the pressure of the three-way pressure compensator is properly increased through the flow regulating device so as to meet the requirement of large-flow output. The invention also has the advantages of simple structure, reliable action, long service life and the like.
Drawings
Fig. 1 is a schematic structural diagram of a first embodiment of the present invention.
Fig. 2 is a schematic diagram of the flow rate adjusting device 2 in fig. 1.
Fig. 3 is a schematic structural diagram of a second embodiment of the present invention.
Fig. 4 is a schematic structural diagram of a third embodiment of the present invention.
Fig. 5 is a schematic diagram showing the relationship between the pilot oil source and the flow rate and the switching area when the control device is operated.
In the figure, 1, a pressure compensator; 2. a flow rate adjusting device; 3. an oil pump; 4. an oil tank; 5. an actuator; 6. a control device; 7. a constant flow valve; 8. a first one-way valve; 9. a first damping; 10. a flow valve; 11. a second damping; 12. a second one-way valve; a1, a first throttling port; a2, a second throttling port; p1, a first working oil source; p2, a second working oil source.
Detailed Description
Embodiments of the invention are further described below with reference to the accompanying drawings:
The pilot-related variable differential pressure compensating system comprises a pressure compensator 1, a first throttling orifice A1, a flow regulating device 2, an oil pump 3 and an oil tank 4, wherein the oil pump is connected with the oil tank and outputs a first working oil source P1, the first working oil source outputs a second working oil source P2 after passing through the first throttling orifice, the second working oil source is respectively connected with an executing element 5 and a pressure compensator spring cavity, the flow regulating device is provided with a closed first state and an opened second state, and when the flow device is in the first state, the elasticity of the pressure compensator spring cavity, the second working oil source entering the pressure compensator spring cavity and the first working oil source in the pressure compensator control cavity are mutually matched to control the opening of a valve core of the pressure compensator; when the flow device is in the second state, the first working oil source is connected with the pressure compensator spring cavity after passing through the flow regulating device, and the elastic force of the pressure compensator spring cavity and the pressure oil entering the pressure compensator spring cavity from the oil outlet of the flow regulating device are matched with the first working oil source in the pressure compensator control cavity to control the opening of the valve core of the pressure compensator. The invention has the beneficial effects that through the arrangement of the flow regulating device, the pressure compensator releases the oil of the constant delivery pump at extremely low pressure during standby, so that the energy consumption of the product is low, and when large-flow output is required, the pressure of the three-way pressure compensator is properly increased through the flow regulating device so as to meet the requirement of large-flow output. The invention also has the advantages of simple structure, reliable action, long service life and the like.
The invention comprises a control device 6 which is respectively connected with the first throttling orifice and the flow regulating device and is respectively used for regulating the flow passing through the first throttling orifice and the flow regulating device. Specifically, the control source of the control device is a pilot oil source, the flow passing through the first throttling orifice and the flow regulating device is regulated by the pressure of the pilot oil source, and the opening pressure of the first throttling orifice is smaller than the opening pressure of the flow regulating device. The control device adopts the pressure oil of the pilot oil source for control, and is convenient, simple and convenient for control and convenient for oil way setting. Of course, different opening flow control can be realized by an electric control mode in the actual production process. The range of adjustment can be reasonably utilized so that the oil liquid of the constant delivery pump is released by the pressure compensator under extremely low pressure when the product is in standby, so that the energy consumption of the product is low, and the pressure of the three-way pressure compensator is properly improved through the flow adjusting device when the high-flow output is needed so as to meet the requirement of the high-flow output.
The opening pressure of the flow regulator and the pressure of the spring cavity of the pressure compensator are not directly related, but rather the size of A2 determined by the opening pressure of the second orifice influences the pressure of the spring cavity of the pressure compensator, namely, as A2 increases, the flow Q2 passing through A2 increases, and thus the flow passing through the first damper also increases, the pressure generated on the first damper also increases, and the increased pressure is added to the spring cavity of the pressure compensator through the communicated accommodating cavity, so that the pressure compensator is closed, and the flow Q1 passing through A1 is further improved, because as the pressure compensator is closed (namely, the pressure compensator orifice is smaller), the pressure of P1 increases, and the difference between P1 and P2 increases, and under the condition that A1 is unchanged, Q1 increases accordingly.
The invention comprises a constant flow valve 7, wherein the second working oil source, the spring cavity of the pressure compensator and the oil outlet of the flow regulating device are all connected with the oil tank through the constant flow valve. The constant flow valve is arranged to drain the pressure oil from the pressure compensator spring chamber TH1 at a small flow rate when the actuator is not operating (when A1 is closed).
The second working oil source is connected with the spring cavity of the pressure compensator through a first one-way valve 8 and a first damping 9. This allows the load pressure (P2) to be picked up without picking up the flow, avoiding affecting the flow at the actuator.
Embodiment one: referring to fig. 1, the flow regulating device comprises a second throttle orifice A2, a flow valve 10 and a second damper 11, wherein the first working oil source is connected with a pressure compensator spring cavity after passing through the second throttle orifice, the flow valve and the second damper in sequence, the first working oil is connected with a flow valve control cavity, the pressure oil of an oil outlet of the second throttle orifice is connected with the flow valve spring cavity, the elastic force of the flow valve spring cavity, the pressure oil at the oil outlet of the second throttle orifice flowing into the flow valve spring cavity and the first working oil flowing into the flow valve control cavity are mutually matched to control the opening of the flow valve, and the control device is connected with the second throttle orifice and is used for regulating the flow passing through the second throttle orifice.
Embodiment two: referring to fig. 3, the flow regulating device comprises a second throttling orifice, a flow valve and a second damper, wherein the first working oil source is connected with the spring cavity of the pressure compensator after passing through the second throttling orifice, the flow valve and the second damper in sequence, the first working oil is connected with the control cavity of the flow valve, the pressure oil of the oil outlet of the second throttling orifice is connected with the spring cavity of the flow valve, and the control device is connected with the spring cavity of the flow valve and is matched with the elasticity of the spring cavity of the flow valve, the pressure oil flowing into the oil outlet of the second throttling orifice of the spring cavity of the flow valve and the first working oil flowing into the control cavity of the flow valve to control the opening of the flow valve.
Embodiment III: referring to fig. 4, the flow regulating device comprises a second throttling orifice, a flow valve and a second damper, the first working oil source is connected with the spring cavity of the pressure compensator after passing through the second throttling orifice, the flow valve and the second damper in sequence, the first working oil is connected with the control cavity of the flow valve, the pressure oil of the oil outlet of the second throttling orifice is connected with the spring cavity of the flow valve, the elastic force of the spring cavity of the flow valve, the pressure oil at the oil outlet of the second throttling orifice flowing into the spring cavity of the flow valve and the first working oil flowing into the control cavity of the flow valve are matched with each other to control the opening of the flow valve, and the control device is connected with the second damper and is used for regulating the flow passing through the second damper.
A second one-way valve 12 is arranged between the flow valve and the second damper. Only the flow valve is allowed to flow out.
The system of the present invention will be further described with reference to the accompanying drawings:
a1: the first throttling port is responsible for generating Q1 for the convenience of description and the flow passing area of the first throttling port is also referred to as the flow passing area in the following, and meanwhile, the flow passing area is increased along with the increase of the pilot oil source;
q1: flow rate generated through A1;
A2: the second choke, for convenience of description, also refers to its flow area in the following, is responsible for generating Q2, and at the same time becomes larger as the pilot oil source increases;
q2: the flow rate generated after passing through the flow rate regulating device;
p1: the first working oil source is used for convenience in description and also refers to the pressure at the first working oil source;
p2: the second working oil source is used for convenience in description and also refers to the pressure at the second working oil source;
First check valve 8: the device is mainly used for load pickup;
second check valve 12: allowing only the flow valve to flow to the second damper 11;
TH1: spring force of the spring cavity of the pressure compensator;
TH2: the spring force of the flow valve spring chamber;
A first damping 9, feedback damping;
second damping 11: dynamic stable damping;
In fig. 3, variable A2 is replaced by variable TH2, and Q2 increases as TH2 increases. Fig. 4 shows the second damping as the OR2 increases, and Q2 increases. The principle is the same as the principle in fig. 1, and the following description is made with reference to fig. 1 and fig. 2 and 5:
Only if Q2 increases, a pressure loss occurs through the first damper 9, so that the pressure of TH1 increases.
The relationship between A1 and Q1 is described below, and the pressures of P1 and P2 are indicated as shown in FIG. 1, when the flow formula is basedWherein C d is the flow coefficient, ρ is the liquid density, A1 is the opening area of the first orifice, ΔP is the pressure difference after passing through the first orifice; and force balance equation for pressure compensator
P1 is the pressure of the first working oil source; p2 is the pressure of the second working oil source; a is the area of the flow passing through the pressure compensator, F TH1 is the spring force of the pressure compensator spring chamber; it can be seen that:
1.ΔP and TH1 are positively correlated, and as long as TH1 is reasonably arranged, ΔP can be basically considered to be unchanged.
2. Q1 and A1 are positively correlated, and Q1 increases as A1 and DeltaP increase. Under certain conditions, assuming that ΔP is unchanged, Q1 is only positively correlated with A1.
For some engineering machinery, when the standby time is long, the pressure of P1 is expected to be low, so that the consumed fuel oil is low, and the heat generation is low, so that the TH1 spring force is set to be low; however, the actuator speed determined for Q1 must also be satisfied, so it is necessary to raise the pressure of P2 when the pilot pressure reaches a certain value, so that the three-way pressure compensator tends to close, introducing more hydraulic oil into A1 to generate Q1, which is the object to be achieved in this patent. As shown in fig. 5, the relationship among A1, A2, Q1, Q2 is defined, and the magnitude of Δp can be determined according to design requirements. When A2 is generated, Q2 is generated, and then Q1 is increased, and if A2 is not generated, the curve of Q1 is Q11. The invention sets the small spring (spring with smaller elasticity), when the system is in standby (when the flow needed by the executive component is smaller), the pressure compensator is at the right position, thus the invention can play the role of low pressure unloading and reducing energy consumption. When the product works normally, the oil inlet pressure is increased by the flow regulating device, so that the pressure compensator tends to be closed, more hydraulic oil is introduced into A1 to generate Q1, and the flow and response speed of the system are ensured. For fig. 3 and 4, the adjustment of A2 may also be by adjusting the flow valve spring chamber pressure or the second damping.
Namely, when both A1 and A2 are 0, the oil of the oil pump is discharged to the oil tank through the three-way pressure compensator at lower pressure, so that the oil pump is in a first state;
when A1 is greater than 0 and A2 is equal to 0, the output flow of Q1 is only positively correlated with A1 (assuming that the three-way pressure compensator differential pressure is constant), which is the second state of the present invention.
When A1> A2>0, Q2 is increased along with the increase of A2, so that the pressure of the spring cavity of the three-way pressure compensator is increased, the pressure difference constant condition (essentially, the pressure difference is increased) of the assumed three-way pressure compensator in the second state is changed, and then Q2 is lifted, and the interval section A2 and A1 simultaneously influence Q1, and A1 is directly increased in area, so that Q1 is lifted; a2 is increased by Q2, which creates a pressure on the first damping 9, which is added to the spring chamber of the three-way pressure compensator, causing it to tend to close, thereby increasing Q2 and thus increasing the flow Q1 through A1, because as the pressure compensator closes (i.e. the pressure compensator is a smaller orifice), the pressure of P1 will rise, resulting in an increase in the difference between P1 and P2, and Q1 will increase with A1, which is the third state of the invention.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. Furthermore, in the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
The skilled person will know: while the invention has been described in terms of the foregoing embodiments, the inventive concepts are not limited to the invention, and any modifications that use the inventive concepts are intended to be within the scope of the appended claims.
Claims (5)
1. The pilot-related variable pressure differential pressure compensation system is characterized by comprising a pressure compensator (1), a first throttling orifice (A1), a flow regulating device (2), an oil pump (3) and an oil tank (4), wherein the oil pump is connected with the oil tank and outputs a first working oil source (P1), the first working oil source outputs a second working oil source (P2) after passing through the first throttling orifice, the second working oil source is respectively connected with an executing element (5) and a pressure compensator spring cavity, the flow regulating device is provided with a closed first state and an open second state, when the flow device is in the first state, the first working oil source is connected with the pressure compensator control cavity, the second working oil source is connected with the pressure compensator spring cavity, and the elasticity of the pressure compensator spring cavity, the second working oil source entering the pressure compensator spring cavity and the first working oil source in the pressure compensator control cavity are mutually matched to control the opening of a pressure compensator valve core; when the flow device is in a second state, the first working oil source is connected with the pressure compensator spring cavity after passing through the flow regulating device, and the elastic force of the pressure compensator spring cavity, the pressure oil entering the pressure compensator spring cavity from the oil outlet of the flow regulating device and the first working oil source in the pressure compensator control cavity are matched with each other to control the opening of the valve core of the pressure compensator;
The hydraulic control device comprises a first working oil source, a second throttling orifice, a flow valve and a second damping, wherein the first working oil source is connected with a pressure compensator spring cavity after passing through the second throttling orifice, the flow valve and the second damping in sequence, the pressure oil of an oil outlet of the second throttling orifice is connected with a flow valve spring cavity, the pressure oil at the oil outlet of the second throttling orifice is connected with the flow valve spring cavity, the elastic force of the flow valve spring cavity, the pressure oil at the second throttling orifice and the first working oil at the oil outlet of the flow valve are mutually matched with each other to control the opening of the flow valve, the control device is connected with the second throttling orifice and is used for adjusting the flow rate passing through the second throttling orifice, the flow control device comprises the second throttling orifice, the flow valve and the second damping, the first working oil source is connected with the pressure oil outlet of the second throttling valve in sequence and is connected with the pressure oil outlet of the flow valve spring cavity, the pressure oil at the oil outlet of the second throttling orifice is mutually matched with the first working oil outlet of the flow valve cavity, the pressure oil outlet of the flow valve is connected with the flow valve spring cavity, the pressure oil outlet of the first working oil at the first throttling valve is mutually matched with the flow valve, the flow valve cavity, the flow control device is connected with the flow valve of the flow valve is connected with the flow valve of the second throttling valve, the flow valve is connected with the flow valve and the flow valve is connected with the flow valve, the flow valve is connected with the flow valve, the flow valve and the second damping are connected with the pressure compensator spring cavity, the first working oil is connected with the flow valve control cavity, the pressure oil of the oil outlet of the second throttling port is connected with the flow valve spring cavity, the elastic force of the flow valve spring cavity, the pressure oil at the oil outlet of the second throttling port flowing into the flow valve spring cavity and the first working oil flowing into the flow valve control cavity are mutually matched to control the opening of the flow valve, and the control device is connected with the second damping and used for adjusting the flow passing through the second damping.
2. The pilot-related variable differential pressure compensation system of claim 1, wherein the control source of the control device is a pilot oil source and regulates flow through the first restriction and the flow regulator by pressure of the pilot oil source, and wherein the opening pressure of the first restriction is less than the opening pressure of the flow regulator.
3. The pilot-related variable differential pressure compensation system according to claim 1, characterized by comprising a constant flow valve (7), wherein the second working oil source, the spring cavity of the pressure compensator and the oil outlet of the flow regulator are all connected with the oil tank through the constant flow valve.
4. A pilot-related variable differential pressure compensation system according to claim 1, characterized in that the second source of working oil is connected to the pressure compensator spring chamber via a first non-return valve (8), a first damping (9).
5. A pilot-related variable differential pressure compensation system according to claim 1, characterized in that a second non-return valve (12) is arranged between said flow valve and the second damper.
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| CN207596344U (en) * | 2017-11-30 | 2018-07-10 | 圣邦集团有限公司 | A kind of multi-way valve equipped with compensator and the control system equipped with the multi-way valve |
| CN208185101U (en) * | 2018-04-18 | 2018-12-04 | 北京华德液压工业集团有限责任公司 | A kind of big flow single channel double overflow three-way pressure compensating device |
| CN109058210A (en) * | 2018-10-26 | 2018-12-21 | 圣邦集团有限公司 | A kind of valve post-compensation system that pressure difference is constant |
| CN212509023U (en) * | 2020-06-29 | 2021-02-09 | 圣邦集团有限公司 | Pilot-associated variable differential pressure compensation system |
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| CN207598616U (en) * | 2017-11-30 | 2018-07-10 | 圣邦集团有限公司 | A kind of multichannel valve control system of variable backoff pressure difference |
| CN207596344U (en) * | 2017-11-30 | 2018-07-10 | 圣邦集团有限公司 | A kind of multi-way valve equipped with compensator and the control system equipped with the multi-way valve |
| CN208185101U (en) * | 2018-04-18 | 2018-12-04 | 北京华德液压工业集团有限责任公司 | A kind of big flow single channel double overflow three-way pressure compensating device |
| CN109058210A (en) * | 2018-10-26 | 2018-12-21 | 圣邦集团有限公司 | A kind of valve post-compensation system that pressure difference is constant |
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