CN1207184A - Pressure compensating hydraulic control valve system - Google Patents
Pressure compensating hydraulic control valve system Download PDFInfo
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- CN1207184A CN1207184A CN 97191641 CN97191641A CN1207184A CN 1207184 A CN1207184 A CN 1207184A CN 97191641 CN97191641 CN 97191641 CN 97191641 A CN97191641 A CN 97191641A CN 1207184 A CN1207184 A CN 1207184A
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Abstract
An improved pressure-compensated hydraulic system for feeding hydraulic fluid to one or more hydraulic actuators (20). A remotely located, variable displacement pump (16) provides an output pressure equal to input pressure plus a constant margin. A pressure compensation system requires that a load-dependent pressure be provided to the pump input through a load sense circuit. A reciprocally spooled, multi-ported isolator transmits the load-dependent pressure to the pump input but prevents fluid in the load sense circuit from leaving the load sense circuit and flowing through a relatively long conduit leading to the remotely located pump. In a multi-valve array (12), at least one valve section (13, 14, 15) has a backflow-preventing shuttle valve which prevents backflow through the pressure compensation system if a main relief valve is operative.
Description
Invention field
The present invention relates to control the valve member of hydraulic machinery, relate in particular to and to keep constant pressure difference to keep the pressure-compensated valve of uniform flux.
Background
The speed of the driven workpiece of hydraulic pressure depends on the cross-sectional area of the main narrow orifice of hydraulic system on machine, and the pressure drop by those narrow orifices.For the ease of control, designed the pressure compensation hydraulic control system and eliminated pressure drop.These previous control system comprise that the pressure with valve working mouth place is delivered to input end on the volume adjustable hydraulic pump so that the detection line of pressurization hydraulic fluid to be provided in system.The self-regulation that pump output produces provides the pressure drop of passing the control aperture of a constant, can be controlled its cross-sectional area by the operating personnel of machine.Because it is constant that pressure drop keeps, only by the cross-sectional area decision in aperture, institute is so that control for the movement velocity of workpiece.Be the U.S. Pat 4,693,272 of " subsequent pressure compensation integral hydraulic valve " here in conjunction with denomination of invention with reference to this system of announcement.
Because operation valve in this system and hydraulic pump can not be provided with usually mutually with adjoining, so, must the information of change of load pressure could be delivered to pump input end far away by flexible pipe or other relatively long conduits.When machine quit work, some hydraulic fluids tended to flow out from these conduits.When operating personnel require to move once more, before pressure compensating system fully comes into force, these conduits must be filled with once more.Because the length of these conduits, the response of pump may lag behind, and the slight decline that may load, and these features are known as " time lag " and " starting descends " problem.
In some hydraulic system, the piston that drives load " reaches minimum point (bottoming out) " and may cause total system " hang up ".This situation may betide uses the maximum functional mouth pressure to come in the system of starting pressure bucking-out system.In this case, the load that reaches minimum point has maximum working hole pressure, and pump can not provide bigger pressure; Therefore pass the control aperture and do not have a pressure drop.As a kind of compensation, this system can comprise a reduction valve in the load detection loop of hydraulic control system.Be in when reaching minimum point, open reduction valve and make detected pressure drop to load detection falling pressure, make pump that one pressure drop of passing the control aperture can be provided.
When this measure is effective, pass in the system of the substantially invariable partial devices of control aperture pressure drop as keeping at working pressure compensation non-return valve, can produce undesirable side effects.Detect the set point of reduction valve even working hole pressure overloads, piston does not reach minimum point, and reduction valve still may be opened.In this case, some fluid will flow through the pressure compensation non-return valve backward from working hole and enter in the pump housing.As a result, load may descend, and this situation can be called as " backflow " problem.
For these reasons, be necessary that device is reduced or eliminate these time lags in some hydraulic system that starting descends and reflux problem.
Technical scheme
Purpose of the present invention satisfies these needs exactly.
The one hydraulic valve assembly that is used for hydraulic fluid is sent at least one load, it comprises: one produces the pump of variable output pressure, and this output pressure equals the input pressure and a constant allowance pressure sum of pump input end at any time.The independent valve unit that the control hydraulic fluid flows to from pump in the hydraulic actuator is connected with a load, and bears the load forces that produces load pressure.The type of valve unit makes and detect peak load pressure in valve unit, is transported to the load detected pressures that pump is controlled the input port to provide one.
Each valve unit has a flow measurement metering-orifice, enters separately actuator by this hole hydraulic fluid from pump.Thereby pump output terminal pressure acts on a side of flow measurement metering-orifice.Pressure-compensated valve in each valve unit provides the load detected pressures at the opposite side of flow measurement metering-orifice, makes the pressure drop of passing the flow measurement metering-orifice be substantially equal to constant allowance pressure.Pressure compensator has a poppet valve core that can slide in vestibule, it is separated into first and second cavitys with vestibule.First cavity is communicated with the opposite side of flow measurement metering-orifice, and second cavity is communicated with the load detected pressures.Pressure differential between first and second cavitys changes the motion that causes poppet valve core as a result, and the size and Orientation of pressure differential has determined the position of poppet valve core in the vestibule.
Vestibule has an output terminal, and fluid is from flowing to corresponding hydraulic actuator here.Poppet valve core has a passage, can flow between flow measurement metering-orifice and output terminal by this passage fluid, and flow is by the determining positions of poppet valve core.When the pressure in first cavity can be realized this flowing during greater than the pressure in second cavity, and, can not realize this mobile when the pressure in second cavity during obviously greater than the pressure in first cavity.
Non-return valve is positioned at poppet valve core and controls pressure communication between first cavity, output terminal and second cavity.In one embodiment of the invention, non-return valve and cuts out this passage when the pressure of output terminal during greater than the pressure in first cavity in the passage of poppet valve core, take this to prevent that fluid flows back to the pump from actuator under the overload pressure.In another embodiment of the present invention, poppet valve core has a guiding channel between first and second cavitys.Here when the pressure in second cavity during greater than the pressure in first cavity, the closure of check ring guiding channel.
Brief description
Fig. 1 is the synoptic diagram that the hydraulic system of multiple valve assembly of the present invention has been installed;
Fig. 2 is the partial side, cross-sectional view that embodies valve of the present invention;
The cross-sectional view of valve among Fig. 3 Fig. 2;
Fig. 4 is the cross-sectional view that is similar to Fig. 3 that another embodiment of the present invention is shown.
The detailed description of preferred embodiment
Fig. 1 illustrates that schematically one has the hydraulic system 10 of the multiple valve assembly 12 of control machine hydraulic power workpiece (as the suspension rod and the suspension bucket of a backhoe) everything.Valve member 12 comprises several independent valve units 13,14 and 15 that connect side by side mutually, are used to control a motion stage of workpiece.The hydraulic fluid that one valve unit of setting 13,14 or 15 controls are flowed out from pump 16 makes it to flow into the several actuators 20 that are connected with workpiece, and then returns in a reservoir or the container 18.Each actuator 20 all has a cylindrical shell 22, has the inside with shell to be separated into the piston 24 of lower chamber 26 and upper cavity 28 in the enclosure.
Typically, pump 16 is away from valve member 12, and makes it to be connected with the feed path 31 that passes valve member 12 by supplying duct or flexible pipe 30.Pump 16 is that the design output pressure equals the variable type pump that discharge capacity control input port 32 pressure add the constant voltage that is called " allowance ".Control input port 32 is connected with the transfer passage 34 of the valve unit 13-15 that passes valve member 12.Reservoir passage 36 also passes valve member 12 and connects with container 18.
For the ease of understanding the present invention, be necessary in an embodiment, according to the basic procedure of a valve unit 14 explanation fluids.Each valve unit 13-15 in the valve member 12 is operation in a similar fashion, and following explanation can be applicable to each valve unit.
See also Fig. 2, valve unit 14 has body 40 and control guiding valve 42, and the operating personnel of machine can be by operating a control assembly (but not shown in the figures) that be fixed on the control guiding valve, in an intrinsic vestibule along reciprocating direction motion control guiding valve.According to the mode of motion of guiding valve 42, hydraulic fluid or oil flow to the lower chamber 26 or the upper cavity 28 of cylindrical shell 22, and take this driven plunger 24 up or down.Here, with upper and lower or wait reference up or down as direction relations and motion, with reference to the accompanying drawings shown in the relation and the motion of directed element, these relations and the motion orientation during may not to be that the present invention is concrete use.The scope of operating personnel's motion control guiding valve 42 of machine is by the work speed decision that is connected with piston 24.
For jigger lifting piston 24, the operating personnel of machine are moved to the left reciprocating type control guiding valve 42.Open passage like this, allow pump 16 (hereinafter under the control of Shuo Ming load sensing network) that hydraulic fluid is pumped out from reservoir 18, and force its pump output duct 30 of flowing through to enter the interior feed path 31 of body 40.Through feed path 31, the flow measurement metering-orifice that fluid forms by the guiding valve recess 44 by control guiding valve 42 is again by feeding passage 43 and the variable orifice 46 (Fig. 3) that formed by pressure compensation non-return valve 48.When pressure compensation non-return valve 48 was in open mode, flow of hydraulic fluid was crossed split channel 50, controlled the passage 53 of guiding valve 42, and then flowed out the lower chamber 26 that working holes 54 enter cylindrical shell 22 by working hole passage 52.Thereby the pressure that is delivered to piston 24 bottoms moves upward it, so just makes hydraulic fluid flow out the upper cavity 28 of cylinder blanket 22.This hydraulic fluid that is pushed out flows in working hole 56, and the working hole passage 58 of flowing through is by passage 59 flow through control guiding valve 42 and reservoir that links to each other with fluid container 18 or container path 36.
In order to move down piston 24, the operating personnel of machine move right and control guiding valve 42, have so just opened the corresponding passage of a cover, make pump 16 that hydraulic fluid is pressed into upper cavity 28, and flow out from the lower chamber 26 of cylindrical shell 22, realize that piston moves down.
If there is not pressure compensator, the operating staff will be difficult to the speed of control piston 24.Causing the unmanageable immediate cause of movement velocity of piston is the flow of hydraulic fluid, and flow is mainly determined by two variablees, i.e. throttling aperture cross-sectional area the most very and the pressure drop of passing these apertures in the flow path.One of throttling aperture the most very is the measurement of discharge recess 44 of control guiding valve 42, and operating personnel can be by moving the cross-sectional area in control guiding valve control aperture.Though this mode can be controlled a variable that helps to determine flow, square root is directly proportional because flow is directly with this intrasystem total pressure drop (mainly taking place when passing guiding valve recess 44), so it still can not provide Optimal Control.For example, add material to the suspension bucket of backhoe and may increase pressure in the cylindrical shell lower chamber 26, this will reduce load pressure and pump 16 provides difference between the pressure.Do not have pressure compensation, the reducing of this total pressure drop will reduce flow, thereby, even when the operating staff makes flow measurement metering-orifice 44 keep a constant cross-sectional area, will reduce the speed of piston 24.
The present invention relates to a kind of pressure compensation mechanism based on the pressure compensation non-return valve 48 in each valve unit 13-15.Main reference Fig. 3, pressure compensation non-return valve 48 have a poppet valve core 60 that can closely reciprocatingly slide in the vestibule 62 of valve body 40, it is separated into vestibule 62 first cavity 64 and the second channel 66 that is communicated with feeding passage 43.Make poppet valve core 60 downward-sloping (along illustrated direction) by one first spring 68 that is positioned at first cavity 64.The upside 70 and the downside 71 of poppet valve core 60 have equal area.Poppet valve core 60 has the center bore 85 of band side direction hole 87, and they form the path by pressure compensation non-return valve 48 together, Here it is above-mentioned variable aperture 46.
Pressure compensation mechanism detects the pressure at each dynamically working mouth place of each valve unit 13-15 in the multiple valve assembly 12, and selects the maximum pressure at these working hole places to act on the discharge capacity control input port 32 of hydraulic pump 16.Finish this by a series of reciprocating valves 72 and select, each in a series of reciprocating valves all is positioned at different valve unit 13 and 14.First valve unit 15 in the series of valves gate cell does not need the reciprocating valve (see figure 1).With reference in figure 1 and 3 as the valve unit 14 of example, the input end of reciprocating valve 72 is (a) feeding passages 43 (by reciprocal passage 74) and (b) connects the put-through channel 76 that has the upstream valve unit 15 of dynamically working mouth pressure from intervening vaive unit 14, in valve downstream.Feeding passage 43 detects 54 or 56 dynamically working mouth pressure, or detects the pressure of reservoir passage 36 when guiding valve 42 mediates.Operation reciprocating valve 72, the put-through channel 76 by valve unit with input end (a) and (b) are located on the reciprocating valve 72 that bigger pressure is delivered to adjacent valve downstream unit 13.
As shown in Figure 1, farthest the put-through channel 76 of valve downstream unit 13 leads to the transfer passage 34 that is connected with pump control input port 32 in a series of reciprocating valves 72.Therefore by said method, maximum pressure is passed to control input port 32 in interior all the dynamically working mouth pressures of valve member.By transfer passage 34, through each valve unit 13-15, maximum dynamically working mouth pressure also will act on second cavity 66 of pressure compensation non-return valve 48, take this this pressure is put on the bottom 71 of poppet valve core 60.
The end 78 of valve member 12 comprises and is used for feed path 31, transfer passage 34 and reservoir passage 36 are connected to aperture on pump 16 and the container 18.This end comprises that also one is used for reducing the reduction valve 80 that is delivered to the superpressure of container 18 in the pump control transfer passage 34.
In order to make hydraulic fluid flow into dynamically working mouth 54 or 56 from pump, the path, variable aperture of leading to pressure compensation non-return valve 48 need partially open at least.In order to realize this state, must move down poppet valve core 60, side direction hole 87 is communicated with divided channel 50.Because the upside 70 of poppet valve core 60 and downside 71 areas equate, so streaming flow 46 places throttling in the aperture compensates pressure in first cavity 64 of valve 48 like this and is substantially equal to maximum functional mouth pressure in second cavity 66.By the feeding passage 43 among Fig. 2, this pressure is communicated with a side of guiding valve measurement of discharge recess 44.And the opposite side of measurement of discharge recess 44 is communicated with feed path 31, and the pump output pressure that feed path is accepted equals maximum workpiece pressure and adds allowance.
As a result, the pressure drop of passing measurement of discharge recess 44 equals allowance.Can detect the variation of maximum functional mouth pressure from the downside 71 of the supply side (passage 31) of measurement of discharge recess 44 and pressure compensation poppet valve core 60.When such variation was reacted, pressure compensation poppet valve core 60 obtained an equilibrium position, made and passed measurement of discharge recess 44, kept load to detect allowance always.
If concrete valve unit (as a 14) working hole pressure is greater than the supply pressure in the feeding passage 43 under the load dynamic regime, hydraulic fluid will be pushed back pump discharge from actuator 20 through pressure compensation non-return valve 48.Close the path by pressure compensation non-return valve 48, the check valve element 82 in the poppet valve core 60 just can prevent this backflow.
Therefore, the operation of pressure compensation non-return valve 48 makes the constant pressure drop that pump allowance pressure is substantially equal to pass measurement of discharge recess 44.
Fig. 4 illustrates another embodiment that does not use a series of reciprocating valves and reach this result.Here, one valve unit 100 has the valve body 102 with a control guiding valve (not shown), the illustrated mode of the mode of operation of guiding valve and the foregoing description is identical, and the feeding passage 43 of control guiding valve is communicated with first cavity 110 in the vestibule 104 of pressure compensation non-return valve 106.Second cavity 112 of valve vestibule 104 is communicated with the transfer passage 34 that leads to hydraulic pump 16 control input ports 32 successively.
Pressure compensation non-return valve 106 is included in and closely lives the multiple poppet valve core 108 that slides and vestibule is divided into first and second cavitys 110 and 112 in the vestibule 104.The upside of poppet valve core 108 and downside area equate.By being positioned at first spring 114 of first cavity 110, make poppet valve core 108 downwards (along illustrated direction).When poppet valve core moves down, between first cavity 110 and divided channel 116 (similar), open path through center poppet valve core vestibule 118 to the divided channel 50 among first embodiment.As mentioned above, this path is the variable orifice of valve unit.
Though preferred embodiment of the present invention has been described, the scope of protection of present invention is not subjected to the restriction of above-mentioned explanation.These embodiment within the scope of the present invention can have multiple other modifications and variations.Therefore the present invention is not limited to above-mentioned explanation, but is determined by following claim.
Claims (15)
1. be used for controlling hydraulic fluid and flow out the hydraulic system that enters into the valve unit array in a plurality of hydraulic actuators having one from a pump, each valve unit have one with a plurality of hydraulic actuators in a work vestibule that is connected, the output pressure that pump produced is the steady state value greater than control input port pressure, the arrangement type of valve unit makes it can record its maximum pressure in working hole, with provide one the load detected pressures, and with it flow to control the input port; Its improvement comprises:
In each valve unit, a pressure-compensated valve provides the load detected pressures on flow measurement metering-orifice one side, and the flow measurement metering-orifice makes the pressure drop of passing the flow measurement metering-orifice be substantially equal to steady state value at the output pressure of opposite side testing pump; Pressure compensator has a poppet valve core that is slidably disposed in the vestibule, take this to form first and second cavitys of vestibule, first cavity is communicated with the flow measurement metering-orifice, and second cavity is communicated with the load detected pressures, wherein the pressure differential between first and second cavitys has determined to be positioned at the position of the poppet valve core of vestibule, vestibule has one fluid is infeeded output terminal in arbitrary hydraulic actuator, poppet valve core have when poppet valve core corresponding to the pressure in first cavity greater than second cavity internal pressure, when being in primary importance, the passage that fluid is flowed between flow measurement metering-orifice and output terminal; And
One between poppet valve core inner control first cavity, output vestibule and second cavity non-return valve of pressure communication.
2. hydraulic system as claimed in claim 1, also comprise a reduction valve, maximum pressure in the working hole is sent to this reduction valve, wherein the pressure in a control input port equal a set point pressure of (a) reduction valve and (b) in the working hole maximum pressure than low value.
3. hydraulic system as claimed in claim 1 also comprises being positioned at the spring that first cavity makes poppet valve core deflection primary importance.
4. one kind can make operating personnel control the hydraulic valve mechanism of flowing in pressure fluid flows to an actuator from a volume adjustable hydraulic pump the flow process, it is subjected to a load forces effect that produces load pressure, pump has the control input port, and can produce output pressure, its output pressure is that hydraulic valve mechanism comprises greater than a steady state value of control input port pressure:
(a) one first valve member that is arranged in juxtaposition and one second valve member, one flow measurement metering-orifice is provided in the fluid path between them, under operating personnel's control, can move a valve member at least to change the size of flow measurement metering-orifice, take this to control flow to the fluid flow of actuator;
(b) be used for detecting actuator load pressure, and load pressure acted on the detecting device of pump control input port;
(c) pressure drop that is used for keeping passing the flow measurement metering-orifice is substantially equal to the pressure compensator of steady state value, pressure compensator has one and is positioned at slidably poppet valve core of vestibule, take this to limit first and second cavitys of vestibule at the opposite side of poppet valve core, first cavity is communicated with the flow measurement metering-orifice, second cavity is communicated with the detected load pressure of detecting device, wherein, pressure differential between first and second cavitys has been determined the position of poppet valve core in the vestibule, vestibule has an output terminal to the actuator accommodating fluid, poppet valve core has a passage, pressure in poppet valve core is in corresponding first cavity is during greater than the primary importance of second cavity internal pressure, and fluid can flow between flow measurement metering-orifice and output terminal by this passage; With
Be positioned at the non-return valve of the passage that passes poppet valve core, be used for pressure when output terminal closing passage during greater than the pressure in first cavity.
5. a hydraulic system as claimed in claim 4 also comprises being positioned at the spring that first cavity makes poppet valve core deflection primary importance.
6. one kind can make operating personnel control the hydraulic valve mechanism of flowing in pressure fluid flows to an actuator from a volume adjustable hydraulic pump the flow process, it is subjected to a load forces effect that produces load pressure, pump has the control input port, and can produce output pressure, its output pressure is a steady state value greater than pump input end pressure, and hydraulic valve mechanism comprises:
(a) one first valve member that is arranged in juxtaposition and one second valve member, one flow measurement metering-orifice is provided in the fluid path between them, can move a valve member at least and advance to change the size of flow measurement metering-orifice under operating personnel's control, the fluid of taking this to control flow to actuator flows;
(b) be used for making load pressure to control the transfer passage that the input port is communicated with pump;
(c) pressure drop that is used for keeping passing the flow measurement metering-orifice is substantially equal to the pressure compensator of steady state value, pressure compensator has one and is positioned at slidably poppet valve core of vestibule, take this to limit first and second cavitys of vestibule, first cavity is communicated with the flow measurement metering-orifice, second cavity is communicated with transfer passage, wherein, pressure differential between first and second cavitys has been determined the position of poppet valve core in the vestibule, vestibule has an output terminal to the actuator accommodating fluid, poppet valve core has a passage, pressure in poppet valve core is in corresponding first cavity is during greater than the primary importance of second cavity internal pressure, fluid can flow between flow measurement metering-orifice and output terminal by this passage, and described poppet valve core has a guiding channel between first and second cavitys; With
Non-return valve in the guiding channel of poppet valve core is used for cutting out guiding channel during greater than the pressure in first cavity when the pressure in second cavity.
7. hydraulic system as claimed in claim 6 also comprises being positioned at the spring that first cavity makes poppet valve core deflection primary importance.
8. be used for controlling hydraulic fluid and flow out from a pump and enter the hydraulic system of the valve unit array in a plurality of hydraulic actuators having one, each valve unit have one with a plurality of actuators in a work vestibule that is connected, the output pressure that pump produced is the steady state value greater than control input port pressure, the arrangement type of valve unit makes it can record its maximum pressure in working hole, with provide one the load detected pressures, and with it flow to control the input port; Improvement in each valve unit comprises:
In each valve unit, a pressure-compensated valve provides the load detected pressures on flow measurement metering-orifice one side, and the flow measurement metering-orifice makes the pressure drop of passing the flow measurement metering-orifice be substantially equal to steady state value at the output pressure of opposite side testing pump; Pressure compensator has a poppet valve core that is slidably disposed in the vestibule, take this to form first and second cavitys of vestibule, first cavity is communicated with the flow measurement metering-orifice, and second cavity is communicated with the load detected pressures, wherein the pressure differential between first and second cavitys has determined to be positioned at the position of the poppet valve core of vestibule, vestibule has one fluid is infeeded output terminal in arbitrary actuator, poppet valve core have when poppet valve core corresponding to the pressure in first cavity greater than second cavity internal pressure, when being in primary importance, the passage that fluid is flowed between flow measurement metering-orifice and output terminal; And
One in the poppet valve core passage when the non-return valve of the pressure of output terminal closing passage during greater than the pressure in first cavity.
9. hydraulic system as claimed in claim 8 also comprises being positioned at the spring that first cavity makes poppet valve core deflection primary importance.
10. a hydraulic system as claimed in claim 8 comprises that also one is used for selecting a series of reciprocating valves of maximum pressure in the working hole of hydraulic system.
11. hydraulic system as claimed in claim 8, it is characterized in that each valve unit also comprises a first input end that reciprocating valve with an output terminal, connects with first cavity and second input port that is connected with the interior reciprocating valve output terminal of different valve units in the hydraulic system.
12. a hydraulic system as claimed in claim 8 also comprises a reduction valve, pressure maximum in the working hole is sent to this reduction valve, the pressure of wherein controlling the input port equal (a) reduction valve set point pressure and (b) the maximum functional mouth pressure than low value.
13. be used for controlling hydraulic fluid and flow out from a pump and enter the hydraulic system of the valve unit array in a plurality of actuators having one, each valve unit have one with a plurality of actuators in a work vestibule that is connected, the output pressure that pump produced is the steady state value greater than a control input port pressure, the arrangement type of valve unit makes it can record its maximum pressure in working hole, so that a load detected pressures to be provided, it is flowed to the control input port; Improvement in each valve unit comprises:
In each valve unit, a pressure-compensated valve provides the load detected pressures on flow measurement metering-orifice one side, and the flow measurement metering-orifice is at the output pressure of opposite side testing pump, equals steady state value on making in the pressure drop of passing the flow measurement metering-orifice; Pressure compensator comprises:
(a) poppet valve core that is slidably disposed in the vestibule, take this to form first and second cavitys of vestibule, first cavity is communicated with the flow measurement metering-orifice, and second cavity is communicated with the control input port of pump, wherein the pressure differential between first and second cavitys has determined to be positioned at the position of the poppet valve core of vestibule, vestibule has one fluid is infeeded output terminal in arbitrary actuator, and poppet valve core has a guiding channel between first and second cavitys; And
One in the guiding channel of poppet valve core non-return valve, when the pressure in second cavity is closed guiding channel with it during greater than the pressure in first cavity.
14. hydraulic system as claimed in claim 13, also comprise a reduction valve, pressure maximum in the working hole is sent to this reduction valve, it is characterized in that, the pressure of control input port equal (a) reduction valve one set point pressure and (b) the maximum functional mouth pressure than low value.
15. hydraulic system as claimed in claim 13 comprises that also one is positioned at the spring that first cavity makes poppet valve core deflection primary importance.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97191641 CN1207184A (en) | 1996-11-13 | 1997-09-30 | Pressure compensating hydraulic control valve system |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US08/747,843 | 1996-11-13 | ||
| CN 97191641 CN1207184A (en) | 1996-11-13 | 1997-09-30 | Pressure compensating hydraulic control valve system |
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| Publication Number | Publication Date |
|---|---|
| CN1207184A true CN1207184A (en) | 1999-02-03 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 97191641 Pending CN1207184A (en) | 1996-11-13 | 1997-09-30 | Pressure compensating hydraulic control valve system |
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| Country | Link |
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| CN (1) | CN1207184A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101482130A (en) * | 2008-01-09 | 2009-07-15 | 胡斯可国际股份有限公司 | Hydraulic control valve system with isolated pressure compensation |
| CN109844325A (en) * | 2016-10-13 | 2019-06-04 | Hydac流体技术有限公司 | The gentle lifting device with this discharge pressure balance in discharge pressure day |
-
1997
- 1997-09-30 CN CN 97191641 patent/CN1207184A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101482130A (en) * | 2008-01-09 | 2009-07-15 | 胡斯可国际股份有限公司 | Hydraulic control valve system with isolated pressure compensation |
| CN101482130B (en) * | 2008-01-09 | 2013-05-29 | 胡斯可国际股份有限公司 | Hydraulic control valve system with isolated pressure compensation |
| CN109844325A (en) * | 2016-10-13 | 2019-06-04 | Hydac流体技术有限公司 | The gentle lifting device with this discharge pressure balance in discharge pressure day |
| CN109844325B (en) * | 2016-10-13 | 2020-09-22 | Hydac流体技术有限公司 | Discharge pressure compensation valve and lifting device comprising such a discharge pressure compensation valve |
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