CN101644259B - Regulating valve used for regulating delivery volume of reciprocating pump - Google Patents
Regulating valve used for regulating delivery volume of reciprocating pump Download PDFInfo
- Publication number
- CN101644259B CN101644259B CN 200810145866 CN200810145866A CN101644259B CN 101644259 B CN101644259 B CN 101644259B CN 200810145866 CN200810145866 CN 200810145866 CN 200810145866 A CN200810145866 A CN 200810145866A CN 101644259 B CN101644259 B CN 101644259B
- Authority
- CN
- China
- Prior art keywords
- valve
- pump
- fluid
- pressure
- piston
- 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
Images
Landscapes
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a regulating valve used for regulating the delivery volume of a rotatory pump, which comprises a valve casing (21), a valve piston (22), a valve spring (25) and regulating equipment (27 and 28), wherein the valve piston (22) is mounted to be capable of moving in the valve casing, and comprises an actuating surface (23) used for valve actuating pressure (P20) of fluid; the valve spring (25) resists the force applied on the valve piston by the valve actuating pressure; and the valve piston can be regulated in the direction of the force applied by the valve actuating pressure or in the direction opposite to the direction of the force applied by the valve actuating pressure through the regulating equipment (27 and 28). The invention also relates to a rotatory pump capable of regulating the delivery volume, which comprises a pump case (1), a delivery chamber formed in the pump case and comprising a fluid inlet (2) on the low-pressure side of the pump and a fluid outlet (3) on the high-pressure side of the pump, a delivery element (5) capable of moving in the delivery chamber to deliver the fluid, and a regulating valve (20) used for regulating the delivery volume and arranged in the fluid delivered by the delivery element (5).
Description
Technical field
The present invention relates to a kind of modulating valve for the delivery volume of regulating rotary pump and the rotary pump that comprises modulating valve, wherein said modulating valve is disposed in the delivery volume that is used for regulating the fluid of being carried by pump in the fluid circulation of pump.Therefore, when being provided for the delivery volume of regulating rotary pump, the invention still further relates to modulating valve itself.
Background technique
Positive displacement pump is to carry fluid with the proportional volume flow of the speed of pump.Revolution or each reciprocal stroke---are so-called specific volume flow---is constant or in fact can be considered at least can be well close to constant.For instance, the constancy of revolution or every stroke and conflicting in some applications with the proportionality of the speed of pump accordingly, in these are used, low in the volume flow that the velocity range internal ratio of one or more pumps is produced by proportionality by the fluid demand that assembly had of separately pump supply.In each velocity range, pump therefore carried exceeded demand and diminished the volume flow that the lost territory guides away.This problem has description in US6126420, it discloses a kind of be used to the internal gear pump with adjustable delivery volume that addresses this problem simultaneously.
US6244839B1 discloses a kind of internal gear pump with adjustable delivery volume equally.For regulating, internal gear can move axially with respect to external gear.Internal gear is a part that moves axially regulon, and this moves axially regulon and is formed in the piston that both sides all can act on.By the 3-position 4-way modulating valve, regulon bears the fluid of being carried by pump.Modulating valve comprises valve casing and valve piston, and described valve piston can move forward and backward in valve casing vertically, and this valve piston bears the fluid that transports and the valve spring power of bearing the pressure of this fluid of opposing at another axial end at an axial end.The position of valve piston is set with the equilibrium of forces that is produced by hydrodynamic pressure according to the power of valve spring.Modulating valve is constructed such that proper when reaching by the predetermined hydrodynamic pressure of valve spring, and the axial position of regulon from the axial position of maximum delivery volume to the minimum delivery volume moves.The bias force of valve spring is set at modulating valve in advance.
WO 03/058071A1 discloses a kind of positive displacement pump, it comprises modulating valve, and the removable valve piston that is used for the delivery volume of adjusting pump in this modulating valve is installed to be the on high-tension side fluid that bears self-pumping in the axial direction and bears the spring force opposite with fluid.In order to reduce the hydrodynamic pressure that pump is adjusted to downwards, a kind of control apparatus for this modulating valve is provided, this control apparatus applies additional force at valve piston.Can quote for the electric stepper motor of the bias force of modulating valve spring with for generation of the magnetic coil of the additional magnetic force example as control apparatus.The direction that the fluid that connects by modulating valve only flows at the maximum delivery volume acts on the mobile unit of pump, and the effect in the opposite direction constantly of on high-tension side pressure.
Summary of the invention
The demand of the assembly that an object of the present invention is neatly and accurately to make the delivery volume of rotary pump and will be supplied adapts, and continues to guarantee to provide sufficient supply to assembly.
The present invention is being used for providing the basis of the rotary pump of fluid to carry out to assembly, described rotary pump comprises pump case, this pump case comprises conveying chamber and the delivery element that can move in this conveying chamber, this delivery element can act directly on the fluid in order to conveying chamber is passed in its conveying.When carry out carrying motion, delivery element can be by oneself or is cooperated or can adopt more other delivery element with another, by increasing the outlet that pressure carries fluid to pass conveying chamber from the entrance of conveying chamber.Entrance is designated as the low voltage side of pump, and outlet is designated as the high pressure side of pump.Pump preferably is arranged in the circulation of enclosed fluid, but can also carry fluid in the circulation of open type fluid in principle.In the time of in being bonded to enclosed fluid circulation, pump enters into conveying chamber in low voltage side withdrawn fluid from reservoir vessel by entrance, and in the high pressure side it is delivered to the assembly that needs the fluid supply or also can is in a plurality of assemblies.In the downstream of one or more assemblies, fluid enters reservoir vessel again, thereby finishes the fluid circulation.For instance, pump can be used to hydraulic pressure that pressure fluid is provided.In a preferred embodiment, pump is mounted or is provided for and is installed in the motor vehicle, in order to be the internal-combustion engine supply Lubricants of driving machine motor vehicle or be automatic transmission sap pressure supply liquid.Preferably, the described pump of described internal combustion engine drive.
Described rotary pump also comprises modulating valve, and by means of this modulating valve, the demand of the assembly that the delivery volume of described pump can be supplied according at least one needs is regulated, and therefore can preferably reduce to drive the energy of this pump.Modulating valve comprises valve casing, the valve piston that can move, valve spring and regulating equipment in valve casing.Valve piston comprises the actuation surfaces (active surface) of fluid valve actuation pressure.Described valve spring is arranged to make it to act on the valve piston, do as a whole with act on valve body on the valve actuation pressure opposite.
In a preferred embodiment, delivery volume is understood that the specific volume flow of pump self---under the situation of rotary pump, be the volume flow of revolution, and be the volume flow of every stroke under the situation of reciprocating piston pump.Although be not most preferred, pump can also be constant pump (constant pump), and modulating valve can be used as the high pressure side that bypass valve is disposed in pump, in order to the fluid of excessive conveying is transported in the reservoir vessel, avoids described at least one assembly.Such bypass is carried the energy consumption that can not reduce pump, but but can guarantee conveying according to demand.In such embodiments, control or adjustment is not the delivery volume in the outlet port of conveying chamber according to demand, but is delivered to the delivery volume of described at least one assembly.By the volume flow of utilizing according to the present invention or the modulating valve of alternate manner is regulated revolution or every stroke, and the part that be branched and that be not used of the volume flow that will carry by pump in the downstream of pump and the upstream of the assembly that is supplied turn back to reservoir vessel, the pump that can regulate self delivery volume can be combined with bypass valve.
In a preferred embodiment, as what directly see from the outlet port of conveying chamber, self delivery volume of pump is regulated by modulating valve.In these embodiments, actuation element is arranged in the pump case movably, and can manage in the direction of its movable (mobility) at the actuation force that its activity direction bears the demand that depends on described at least one assembly.Actuation element specifically is set in the face of the positive of delivery element or around delivery element.In first kind of distortion, actuation element and delivery element are the parts of regulon, wherein said regulon can move forward and backward as an integral unit in pump case, for example can be linear mobile or otherwise pivot rotate or mobile regulon, transverse to the running shaft that is preferably rotatable delivery element.For instance, the example of this regulon is described in US6283735B1 for outer shaft pump (external-axle pump), in US6126420 and US6244839B1, be described for interior axle pump (internal-axle pump), and in EP1262025A2, be described pump for two types.In second kind of distortion, actuation element can be regulated with respect to delivery element and pump case.Actuation element in second kind of distortion specifically can be the actuating ring around delivery element, as known in comprising the wing pump of vane pump, swing type shuttle block pump (pendulum slider pump) and internal gear pump, so as for example by actuation element linear back and forth or pivotal movement regulate off-centre with respect to delivery element.
Actuation force preferably fluid ground produces, because actuation element is formed with the power piston that bears pressure fluid.This pressure fluid can be branched in the high pressure side of pump specifically and return actuation element as the shunting of the volume flow of being carried by pump via modulating valve, and described volume flow of being carried by pump is done as a whole.But in principle, the pressure fluid that actuation element bears can also be one other fluid, for example from the pressure reservoir vessel or from the fluid of another pump supply.
In the another kind distortion, the shunting of fluid is back to low voltage side by modulating valve and enters conveying chamber, and is in order to increase the fill level of conveyor chamber wherein, for example disclosed in US6935851B2.Be back to and fill conveyor chamber and also regulate simultaneously delivery volume, wherein such adjusting can with other type of quoting before in one combine and realize.
According to the present invention, regulating equipment is formed and makes it can be on the direction that is applied to the power on the valve body by the valve actuation pressure or at the direction adjusted valve piston opposite with the valve actuation pressure.It is preferably by electromagnetism work.Identical with other place here, word " or (or) " comprises the implication of " not being ... be exactly ... (either ... or ...) " and the implication of " with (and) " in meaning of the present invention, as long as the implication that limits according to corresponding contents not necessarily.Thereby, regulating equipment can be constructed to make it only to offset the valve actuation pressure or preferably only offset the power of valve spring on identical direction, and replacedly, it can also be constructed to make it both can be along also can be at direction adjusted valve piston in contrast on the direction of valve actuation pressure.
In first preferred embodiment, valve actuation pressure and by the power one that regulating equipment the is applied to valve piston opposing valve spring power that works.If the valve actuation pressure increases, then valve piston can be conditioned by the relative less power of the regulating equipment opposite with valve spring power.
In second preferred embodiment, regulating equipment both is constructed on the direction of valve actuation pressure also at the direction adjusted valve piston opposite with the valve actuation pressure.If regulating equipment is for only comprising the magnetic regulating equipment of an independent magnetic coil, then in these embodiments, the polarity of magnetic coil can be reversed.Replacedly, can each direction in two activity directions of valve piston provide a dedicated magnetic coil, each coil comprises armature, and one in these armatures applies power to valve piston on an activity direction of piston, and another armature applies power to valve piston on another activity direction of valve piston, in order to move forward and backward valve piston.
At least in a second embodiment, preferably equally in first embodiment, therefore the position of valve piston can be regulated and have nothing to do in the valve actuation pressure that acts on the actuation surfaces with respect to valve casing, therefore can set the delivery volume of pump.Therefore modulating valve can be set delivery volume adaptively in the bigger operating range of the assembly that is supplied, constantly or as required increment is adjusted the specified pressure that drops to and not only be adapted to delivery volume.
The control apparatus or the adjustment equipment that are used for this modulating valve are constructed such that preferably delivery volume can utilize this modulating valve to regulate adaptively in the whole operation scope of assembly.On the contrary, the valve actuation pressure of the power of valve spring and lasting opposing valve spring valve has guaranteed the reliable supply to assembly, even---under the situation that regulating equipment lost efficacy---only adjust delivery volume according to the spring constant of bias force and valve spring, as known in traditional rotary pump.Even the present invention will combine with the security of supply that can both guarantee when regulating equipment lost efficacy to the accurate and flexible adaptability of demand; It provides so-called secondary control or secondary adjustment to delivery volume.
Regulating equipment is preferably Proportional valve.It is preferably automatically controlled.Described regulating equipment is magnetically effect preferably.It can comprise the ratio magnetic coil, and this ratio magnetic coil is that Control of Voltage or voltage are adjusted or Current Control or electric current adjustment, namely changes voltage or the electric current that applies by the demand according to described at least one assembly.In other preferred embodiment, modulating valve is by modulating pulse control or adjustment.When using the Sampling modulating valve, can change the endurance of the individual pulse that activates variable or the time lag between two continuous impulses, it also comprises such a case, i.e. the time lag between the endurance of pulse or two continuous impulses all changes according to demand.The endurance in cycle that activates variable is preferably constant.Preferably, use the pulse duration modulation modulating valve.The endurance in cycle of the actuating variable of modulating valve obviously is less than the minute constant (determing time constant) for the rotary pump of regulating delivery volume.Sampling has utilized the low-pass characteristic of pump.On time by changing pulse duration modulation according to demand or under the situation of PFM Pulse Frequency Modulation, change the time lag, by the flow of modulating valve and therefore the delivery volume of rotary pump can almost be controlled or be adjusted according to the electric current demand of assembly constantly.
Modulating valve is preferably and comprises at least three ports, the manifold valve of four ports preferably.It can preferably be changed at least two dislocations, preferably changes at least three dislocations.
In a preferred embodiment, modulating valve is controlled or is adjusted according to the nominal value of the nominal value that will be rotated the volume flow that pump carries or the fluid supply pressure that will be generated by rotary pump.The nominal value that presets pre-determines the control apparatus that is provided for modulating valve or the nominal value of regulating equipment.Nominal value preferably changes according to the demand of assembly.Preferably, characteristic diagram is that the nominal value that depends on the assembly operation state pre-determines.Described at least one nominal value or preferably a plurality of nominal values pre-determine according to physical descriptor, described physical descriptor is the feature of serviceability and is to rely on detection facility to use sensor to find out in the operating process of assembly to obtain.Described at least one physical descriptor specifically can be the load condition of temperature, rotational speed or assembly.Preferably, one or more nominal values of volume flow or fluid supply pressure pre-determine according at least two variablees that embody the assembly operation status flag.If rotary pump is used as the lubricating pump of internal-combustion engine, for instance, the temperature of the cooling liquid in the temperature of lubricant oil or the part of internal-combustion engine or rotational speed or the position of accelerator pedal or throttle valve can utilize sensor to detect---for load condition---, and corresponding nominal value can be determined on the basis of characteristic diagram and can be determined in advance at the control apparatus or the adjustment equipment that are used for modulating valve thus.
In first preferred embodiment, modulating valve is only controlled according to each nominal value.The step that detects the actual value of the physical descriptor that forms nominal value is omitted, any well-designed process for the adjustment of carrying out on the basis of nominal value/actual value comparison also is omitted, wherein said physical descriptor is the representative of described demand, i.e. volume flow or fluid supply pressure.
In same preferred second preferred embodiment, modulating valve is relatively adjusted according to each nominal value of volume flow or fluid supply pressure and the nominal value/actual value between the actual value, and described actual value measures continuously or in a time lag of enough lacking.It is favourable adjusting under following situation, has namely changed the demand of the volume flow of assembly in the working life of assembly owing to loss.
In two embodiments' selectable combination, provide the calibration equipment that can become from the control according to first embodiment according to second embodiment's adjustment, if wherein preferably modulating valve is at first controlled according to predetermined volume flow, owing to the leakage that causes along with component wear forms loss, it becomes the pressure adjustment subsequently.In another embodiment, provide the adaptability calibration equipment, this equipment can be measured the increase of wearing and tearing on the basis of using sensor detection volume flow or fluid supply pressure and change the characteristic diagram of nominal value or nominal value with at least one increment or a plurality of incremental adaptations ground, as continuance of application in the working life of assembly.
In a further advantageous embodiment, modulating valve is on the one hand controlled and is adjusted by electric current in addition on the basis of the characteristic diagram of the nominal value of fluid supply pressure or volume flow or nominal value.Especially preferred embodiment modulating valve for being controlled and regulated by electric current in addition on the basis of the characteristic diagram of the nominal value of fluid supply pressure or volume flow or nominal value by means of pulse duration modulation.The change of the resistance of magnetic regulating equipment is advantageously come balance by electric current adjustment.The electric current that obtains in the magnetic regulating equipment is detected, and since the change that resistance changes the electric current magnitude that produces by according to the variation adjustment duty of obtaining electric current balance recently.But correspondingly, this not only can carry out in the preferred embodiment as the pulse duration modulation modulating valve, can also carry out in the modulating valve of otherwise control.Regulate by also carrying out electric current beyond controlling on the basis of the characteristic diagram of the nominal value of volume flow or fluid supply pressure or nominal value, can omit the adjustment to volume flow or pressure, although or even under the situation of electric current adjustment, can use adjustment to volume flow or pressure extraly.
Control apparatus or adjustment equipment can be integration sections of modulating valve, and it can be installed separately with modulating valve.Nominal value presets the target part that can be considered to control apparatus or adjust equipment, perhaps can be objectively thought respectively that other parts with control apparatus or the equipment of adjustment are separated.Modulating valve is preferably an integration section of rotary pump, and it can be installed on the pump case for instance.In described integrated embodiment, modulating valve can advantageously be arranged in the housing of rotary pump equally, for example forms in the holding space in addition in receiving bore or on the wall of pump case.In these embodiments, the port of modulating valve can form the hole in the mode of saving space and saving in weight or form passage in addition in housing, especially on the described wall of housing.Therefore, pump case can form valve casing equally simultaneously or only form the part of valve casing.
In the embodiment that the delivery volume of pump is directly regulated, advantageously, if actuation element is formed the two-way function power piston that comprises two piston faces, wherein said two piston faces vertically each other opposing and away from and preferably along opposite direction each other opposing and away from, and no matter be this or another piston face or also can be two piston faces, can bear the pressure fluid of pressurization by modulating valve.
If actuation element forms the power piston that can bear pressure fluid, for example only can bear the piston of pressure fluid or two-way function piston preferably in a side, then in a preferred embodiment, it bears the spring force that is applied by pump spring, and wherein pump spring acts on the direction of the delivery volume that increases pump.If actuation element forms the two-way function piston, if thereby preferably pump spring is enough weak makes the adjusting dynamic characteristic of pump can not influenced fatefully by pump spring, but ad hoc or at least to a large extent influenced by deciding property of modulating valve ground.In such embodiments, can also omit pump spring in principle.On the contrary, it is favourable using more weak pump spring, and wherein this pump spring is constructed such that it only can guarantee when rotary pump moves under low speed, can transfer pump under this speed maximum delivery volume.Pump spring applies corresponding to the spring force of the maximum hydrodynamic pressure of 1bar just enough at actuation element.
Be directed to by modulating valve for the purpose of regulating---controlled or be adjusted---to the fluid of rotary pump or when modulating valve only is used as bypass valve from being divided to the fluid of reservoir vessel, preferably when it flows through modulating valve, produce the valve actuation pressure.In such embodiments, need be for generation of the independent port of valve actuation pressure.Enter the port that the identical port of entrance that this modulating valve passes through can form the fluid that produces the valve actuation pressure equally with the fluid that flows through modulating valve.
If preferably the valve actuation pressure produces by a plurality of actuation surfaces, preferably accurately be two actuation surfaces, wherein there is difference in these actuation surfaces in following this mode dimensionally, and this mode makes the valve actuation pressure apply different power according to the different area of actuation surfaces at valve piston.The feature of different power especially preferably combines with supplementary features, and according to described supplementary features, fluid produces the valve actuation pressure when flowing through modulating valve.
In a kind of development was widened, when rotary pump was carried fluid, the bias force of valve spring can be conditioned, and is conditioned with being preferably fluid.So described modulating valve can comprise another piston that preferably only is used to set bias force, and this piston preferably bears the fluid that also produces the valve actuation pressure, wherein can be produced by the fluid of the process that flows for the power that provide the port of separation for the piston of regulating bias force or preferably act on this regulating piston.
Favourable feature equally below dependent claims and in conjunction with in be described.
Description of drawings
Below the basis of one exemplary embodiment of the present invention at accompanying drawing made an explanation.The disclosed feature of exemplary embodiment, any combination of each independent feature and feature has advantageously developed claim and previously described embodiment's theme.Shown in it be:
Fig. 1 is the cross section of positive displacement pump;
Fig. 2 is the longitudinal section of positive displacement pump;
Fig. 3 is the positive displacement pump that comprises for the modulating valve of the delivery volume of regulating pump;
Fig. 4 is with the modulating valve shown in the legend; And
Fig. 5 is the longitudinal section of modulating valve.
Embodiment
Fig. 1 shows the cross section of positive displacement pump (displacement pump).In pump case 1, be formed with and comprise the entrance 2 that is positioned at low voltage side and the conveying chamber that is positioned on high-tension side outlet 3.First delivery element 4 and second delivery element 5 are arranged in the conveying chamber movably.Delivery element 4 and 5 is carried joint each other.Carrying when driven under the jointing state when delivery element 4 and 5, they carry out such conveying campaign, namely by entrance 2 for example the fluid of lubricant oil or hydraulic fluid suck in the conveying chamber and with its with higher pressure from exporting 3 discharges.Delivery element 4 is driven, and is carrying driving delivery element 5 under the jointing state.
Positive displacement pump in the exemplary embodiment is external gear pump.Therefore, delivery element 4 and 5 is the conveying solid of rotation with exterior periphery tooth, and described conveying joint is indented joint.Delivery element 4 and 5 is installed to be and makes that they can be respectively around running shaft R4 and R5 rotation.When they were driven in rotation, the fluid that sucks was transferred from entrance 2, entered the formed conveyor chamber of each backlash by delivery element 4 and 5, passed so-called leg 1a, and was discharged from by exporting 3.
For the delivery volume that can make pump adapts to the requirement of the assembly will be supplied fluid, axial length-joints that can engage the conveying of the delivery element 4 that measures along running shaft R4 and R5 and 5 grown
Degree---adjust.For adjusting, delivery element 5 can be axially to move forward and backward with respect to delivery element 4 and pump case 1 between the position of maximum delivery volume and the position that minimum bonding length is the minimum delivery volume at maximum bonding length.
Fig. 2 shows the longitudinal section of described positive displacement pump.Delivery element 4 non-rotatably is fastened on the live axle, and described live axle stretches out and is supported with driving wheel for driven pump from pump case 1.Delivery element 5 is the part of regulation unit, and this regulation unit also comprises except delivery element 5 by two power pistons 6 and 7 actuation elements of forming.This regulation unit 5-7 can be used as a complete unit and moves forward and backward vertically in pump case 1, in order to can adjust bonding length.Delivery element 5 is arranged between power piston 6 and 7 vertically. Actuation element 6,7 so assembling delivery element 5 can enough rotate around spin axis R5.Regulation unit 5-7 is housed inside in the cylindrical cavity of pump case 1.Described cavity is that the motion of regulon 5-7 forms axial track.It also forms a pressure space 8 in the axle side of regulation unit 5-7, and forms another pressure space 9 at opposite side.Except owing to leak the inevitable loss cause, power piston 6 with 7 with pressure space 8 with 9 each other fluid ground separate and they separated with conveying chamber fluid ground.In the exemplary embodiment, pressure space 8 and 9 can be pressurizeed by pressure fluid respectively, and described fluid is carried by positive displacement pump.Pump spring 10 is arranged in the pressure space 9, and the spring force of wherein said spring acts on the regulon 5-7 in the direction along maximum bonding length, namely on the power piston 7.
Fig. 3 shows the positive displacement pump in the enclosed fluid circulation that is combined in motor vehicle lubrication oil circulation for example.The fluid circulation comprises reservoir vessel 11, pump passes through entrance 2 draw fluid from this reservoir vessel 11 in low voltage side, and with its in the high pressure side with high pressure by export 3, attached supply line 12 and be transported to assembly 14 places that need the fluid supply by cooling and the cleaning equipment 13 that comprises cooler and filter, for example be used for the internal-combustion engine of driving machine motor vehicle.In the downstream of assembly 14, fluid turns back in the reservoir vessel 11 by pipeline 15.
In the downstream of cooling and cleaning equipment 13, be the downstream of the purification part of cooling and cleaning equipment 13 specifically, but still in the upstream of assembly 14, the shunting 16 of fluid is bifurcated and return pump via modulating valve 20.Modulating valve 22 comprises entrance, the outlet that is shorted to reservoir vessel 11 and two other ports of shunting 16, and one of them port is connected to pressure space 8 via pipeline 18, and the another port is connected to pressure space 9 via pipeline 19.Modulating valve 20 is the multitube changing valve.In first dislocation, its guiding shunting 16 enters pressure space 8 and pressure space 9 is connected to reservoir vessel 11, that is, it is connected to pressure space 9 in the external pressure.Second dislocation of the modulating valve 20 that adopts at Fig. 3, it enters pressure space 9 by guiding shunting 16 and makes pressure space 8 and reservoir vessel 11 short circuits (shorting) make these conditions counter-rotatings.Modulating valve 20 in the exemplary embodiment can adopt three dislocations, two positions and a neutral position of just enumerating previously, make that pressure space 8 is separated from one another with 9 and make them separate with shunting 16 with reservoir vessel 11 at this neutral position adjusted valve 20, remove like this owing to leak outside the loss that spills and supervene that causes, the pressure separately in the pressure space 8 and 9 remains unchanged.In the exemplary embodiment, can select three-position four-way valve (4/3-port valve) as modulating valve 20.
Fig. 4 shows modulating valve 20 among Fig. 3 with legend, but is the method for expressing that amplifies.Four ports of modulating valve 20 are illustrated, and the entrance that wherein is used for shunting 16 backflows is represented with I, represents with O to the outlet of reservoir vessel 11, represent with A for the port of pressure space 8, and represent with B for the port of pressure space 9.
Modulating valve 20 is Proportional valve, and the valve actuation pressure P20 that it demonstrates the fluid of homeostatic process just shunt in 16 the pressure of the fluid that is refluxed, and it comprises the valve spring 25 that is arranged for opposing valve actuation pressure P20.When modulating valve 20 was working properly, the valve actuation pressure P20 of fluid and the power of valve spring 25 can not be determined the position of conversion separately.Modulating valve 20 comprises the regulating equipment as Proportional valve, and this regulating equipment is according to the fluid demand of assembly 14 and modulating valve 20 is transformed in another dislocation from a dislocation.If the ratio regulating equipment lost efficacy, then valve actuation pressure P20 and valve spring 25 make modulating valve 20 have the fail safe characteristic.
Regulating equipment is the magnetic regulating equipment that is connected to the electronically actuated signal of pulsewidth modulation.Actuated signal is generated by the form of control apparatus with rectangular signal, and described rectangular signal has last signal level and following signal level and the specific endurance in cycle of constant for example voltage level.The endurance of last signal level is that the endurance of on time (on-time) and the following signal level that causes thus is can change according to pulsewidth modulation turn-off time (off-time).The magnetic force of regulating equipment changes according to the dutycycle of actuated signal, and this dutycycle is the ratio between on time and endurance in the cycle t.The dislocation of modulating valve 20 can from equilibrium of forces and two reaction forces of the power of valve spring 25, i.e. fluid force and the magnetic force that is produced by valve actuation pressure P20, in draw.Valve actuation pressure P20 is more big, and then corresponding with equilibrium of forces magnetic force is just more little.If the summation of fluid force and magnetic force has surpassed spring force, then valve piston 22 is mobile in the direction of first dislocation, and the delivery volume of positive displacement pump is conditioned.If the power of valve spring 25 is preponderated, then valve piston 22 moves to second dislocation, and regulon 5-7 is therefore mobile in the direction of maximum delivery volume.
In a kind of improvement, are assigned on time and turn-off time first and second dislocations of modulating valve 20.When the modulating valve proper functioning, the position of valve piston 22 and therefore the dislocation of modulating valve 20 be not subjected to the influence of valve actuation pressure P20.By way of example, it is contemplated that in each on time, modulating valve 20 adopts first dislocation, be back to pressure space 8 at the fluid of this position shunting 16; And in each turn-off time, modulating valve 20 adopts second dislocation, and the above fluid is back to pressure space 9 in this position.
Because endurance in the cycle t of actuated signal is shorter than the crash time constant of pump significantly, by changing on time and turn-off time, in two embodiments, all can change the flow that flow to each pressure space 8 or 9 by modulating valve 20 in fact constantly.Therefore, can change pressure in the pressure space 8 and the pressure in the pressure space 9 equally constantly.
Regulon 5-7 therefore can be along its axial adjustment path movement and be maintained on any axial position.Therefore delivery volume can adapt to the fluid demand of assembly 14 constantly flexibly and accurately between minimum and maximum delivery volume.
In be provisioning component 14 according to demand, characteristic diagram is stored in the control system of assembly 14---being engine control system in the exemplary embodiment---the electricity or optics storage.For each serviceability of the assembly relevant with fluid demand 14, characteristic diagram comprise fluid supply pressure P14's or in each serviceability the predetermined nominal value of assembly 14 desired volume flow V14.These volume flow nominal values or pressure nominal value are stored in the characteristic diagram according to the physical descriptor that characterizes serviceability, and wherein said serviceability can be distinguished according to fluid demand.Temperature T, rotational speed D and load L quotability are as the example of physical descriptor.Assembly 14 comprises the physical descriptor for detection of one or more sign different operating states.For instance, at the cooling fluid that is used for cooling package 14 or in the fluid of being carried by pump 3, temperature T can measure at the critical localisation of assembly 14.Rotational speed D can detect at an easy rate by tachometer, and the position of load L by accelerator pedal or throttle valve also can detect at an easy rate.According to detected variable, default nominal value is selected pressure nominal value or the volume flow nominal value of formulation on the basis of characteristic diagram, and sends it in the control apparatus of modulating valve 20.Control apparatus forms actuated signal according to current flow ratings, i.e. ratio between on time and endurance in the cycle t.As long as the actual flow demand of assembly 14 is corresponding with nominal value, then need be by means of Moderator Variable the feedback of---being the fluid supply pressure P14 that measures or the actual value of volume flow V14 in present case---.
Control on the basis of nominal value especially can be replenished by the electric current regulated quantity.Electric current is regulated the concrete change that is used for the resistance of compensation magnetic regulating equipment, the change of the resistance that takes place during as temperature change especially, and the electric current that wherein obtains in regulating equipment is detected and be retained as a particular current by detection facility.If detection facility detects the variation of the electric current that obtains and the resistance variations of corresponding regulating equipment, then dutycycle is changed by this way, and this mode makes that the electric current that obtains is corresponding with resistance variations current value before again.
If the real fluid demand of assembly 14 changes and depart from from the nominal value of characteristic diagram, for example owing to the wearing and tearing in the life time of assembly 14 cause, also provide adjustment equipment for modulating valve 20.Described adjustment equipment is formed for the actuated signal of modulating valve 20 according to the nominal/actual value comparison based on assembly 14 required fluid supply pressure P14 or volume flow V14.Adjustment equipment can use storage, and other nominal value of pressure P 14 or volume flow V14 is stored in this storage with the form of the characteristic diagram that can compare with the characteristic diagram that up to the present is used to control.The characteristic diagram of pressure nominal value or volume flow nominal value can be stored in the zones of different of physically different storagies or same storage.Provide senior calibration equipment (superordinate checking device) simultaneously, the demand that detects assembly when it has fully been changed when having made the characteristic diagram of nominal value can not fully describe actual demand, when for example increasing demand owing to wearing and tearing, the part of the control apparatus that this senior calibration equipment can be pressure or volume flow or the equipment of adjustment and the control of change to adjusting.Comparison for nominal/actual pressure, for instance, actual main fluid supply pressure P14 can or---in the example at internal-combustion engine---go up measured obtaining at engine pipeline (engine gallery) on the position in the downstream of the consumption on the assembly 14, and can with to each serviceability all very crucial pressure nominal value compare, for example compare by the difference of seeking between nominal value and the reality.
As described by example, by feedback pressure or volume flow do not controlled and to be developed into by using separately pressure nominal value or volume flow nominal value relatively to adjust pressure or volume flow with the nominal value/actual value between the actual value that records for comparison.A plurality of characteristic diagrams of volume flow V14 or fluid supply pressure P14 can be stored in advance, these characteristic diagrams have been described the demand on the different time points of assembly 14 in Life cycle, for example for first n kilometer of motor vehicle or the characteristic diagram of n hours run of assembly 14, the ensuing m kilometer of vehicle or ensuing m hours run of assembly etc.In this embodiment, can on the kilometer reading of for example vehicle or the basis of record of operation endurance, be changed to next characteristic diagram etc. from the characteristic diagram that at first uses.Finally, control apparatus equally can be according to the state of assembly 14, preferably change the nominal value of characteristic diagram according to each state of assembly 14, in order to can come regulating and controlling valve 20 based on the characteristic diagram after changing respectively.Advantageously, the nominal value of characteristic diagram is automatically changed, or one or more predefined characteristic diagrams are automatically selected, for example according to the kilometer reading of quoting before or operation endurance, or compare according to test fluid supply pressure P14 and with the predetermined nominal value of itself and characteirstic element diagram form, wherein such nominal value/actual value relatively can be used to adjust the pressure of modulating valve 20, but preferably it only be used for is selected to be used to or change the pressure nominal value of an independent predefined characteristic diagram or the Pressure characteristics of volume flow nominal value is wanted sketch map or volume flow characteristic diagram, control being used for.
In Fig. 3 and 4, another shunting 17 was branched out before modulating valve 20 from the shunting 16 that is refluxing, in order to produce valve actuation pressure P20, and the also change thereupon of the valve piston of modulating valve 20, opposite with valve spring 25.
Fig. 5 shows the longitudinal section of carrying out improved modulating valve 20 with respect to generation valve actuation pressure P20.Different with the modulating valve among Fig. 4, valve actuation pressure P20 produces by additional shunting---shunting 17 among Fig. 3 and 4---, but by being controlled or controlled shunting 16 through-flow produce.Remove these and improve, be equally applicable to improved modulating valve 20 about the statement of the modulating valve 20 of Fig. 3 and 4, and the statement of this aspect equally also is suitable for the modulating valve 20 of Fig. 3 and 4.
Modulating valve 20 comprises valve casing 21 and the valve piston 22 that can axially move forward and backward along centre valve axis S in valve casing 21.Also show magnetic coil 27 and the armature 28 of the regulating equipment that is formed by soft iron.Show magnetic coil 27 and the armature 28 of the controlling device that forms with soft iron.Also show the electric contact of magnetic coil 27 simultaneously.Magnetic coil 27 is fixedly connected on the valve casing 21 and around described armature 28.Thereby armature 28 is connected to it can not be moved axially, and valve piston 22 and armature 28 are done as a whole execution and moved axially like this.
Valve piston 22 comprises for first actuation surfaces 23 of valve actuation pressure P20 and second actuation surfaces 24.Axially limit fluid space 26 and boths' actuation surfaces 23 and 24 face with each other together.Actuation surfaces 23 is greater than actuation surfaces 24, and valve actuation pressure P20 is at these actuation surfaces 23 opposing valve springs 25, and wherein in Fig. 5, both ratios have been exaggerated.In fact very little of both size difference, but be restricted to the differential force that makes valve actuation pressure P20 apply the power of and opposing valve spring 25 corresponding with the difference in size of actuation surfaces 23 and 24 constantly at valve piston 22.Since valve piston 22 can be very accurately according to actuation surfaces 23 and 24 different manufacturing of size, therefore described differential force can correspondingly less and valve spring 25 also can be advantageously than more soft in the exemplary embodiment of Fig. 4.Regulating equipment 27,28 correspondingly requires less power.Modulating valve 20 is done as a whole more responsive, and also can be reduced the conversion time of modulating valve 20.
In all dislocations of modulating valve 20, lead to fluid space 26 corresponding to the entrance I of the fluid that will be controlled or adjust.In the corresponding dislocation of the dislocation of the modulating valve 20 in shown and Fig. 3 and 4, port B leads to fluid space 26, and valve piston 22 is with fluid space 26 and therefore entrance I is separated with another port A.Therefore the fluid of shunting 16 is back in the pressure space 9, and pressure space 8 is connected to reservoir vessel 11 via port A and therefore is not connected with pressure.In this dislocation, port A is connected to outlet O via the space that is provided with valve spring 25 in the valve casing 21, and is connected to reservoir vessel 11 via outlet O.Magnetic coil 27 is supplied electric current and shifts armature 28 in the axial direction---to become high signal level from low-signal levels in the exemplary embodiment---if actuated signal has been changed its signal level, opposite with the power of valve spring 25, at first armature is transferred to the intermediate conversion position, given correspondingly one period on time of length, arrive in another limit dislocation first dislocation.In the intermediate conversion position, valve piston 22 is separated two port A and B and fluid space 26, and wherein entrance I still leads to this fluid space 26.In first dislocation, valve piston 22 takes an axial position to make fluid space 26 axially all overlapping with entrance I and port A, and valve piston 22 fluid ground on described axial position separates port B with fluid space 26 fluid ground simultaneously.In first dislocation, shunting 16 fluid is guided through fluid space 26 and port A, enters pressure space 8, and pressure space 9 by valve piston 22 port B and port C be connected to outlet O and go up and finally be connected on the reservoir vessel 11.
Described valve piston 22 is hollow.Hole C be formed at valve piston 22 on the direction of armature 28 near on the cyclindrical surface region of actuation surfaces 24, and its circumferential surface with valve casing 21 forms regulating equipment 27, the 28 narrow sealing off gap that separate with fluid space 26 fluid ground.The cyclindrical surface region of valve piston 22 equally radially is attached on the actuation surfaces 23 in the outside and away from regulating equipment 27,28, and as long as modulating valve 20 does not adopt first dislocation just to form another narrow sealing off gap with valve casing 21, valve piston 22 adopts the overlapping axial position of fluid space 26 and port A on this primary importance.
The regulating equipment 27,28 that comprises specified control equipment connects modulating valve 22 in the whole operation scope of assembly 14, and control or adjust the axial position of regulon 5-7, and therefore in the gamut inner control of provisioning component 14 desired volume flows suitably or adjust the delivery volume of positive displacement pump.If regulating equipment 27,28 or specified control equipment owing to fault lost efficacy, for example because cable disconnects or power plug connects separately, then the valve actuation pressure P20 of fluid and valve spring 25 can be used as standby management.Modulating valve 20 is constructed to make and occurring under the situation about losing efficacy, in case the fluid supply pressure P14 that reaches greater than the maximum fluid supply pressure P14 that when modulating valve 20 is working properly, sets, then the delivery volume of pump is only regulated from being up to minimum direction.For this purpose, valve spring 25 is installed to be to have than being applied to the bigger bias force of power on the valve piston 22 at the maximal valve actuation pressure P20 that passes through that sets under the situation of proper functioning.
Reference numbers
1 pump case 1a leg
3 outlets of 2 entrances
4 delivery elements, 5 delivery elements
6 power pistons, 7 power pistons
8 pressure spaces, 9 pressure spaces
10 pump springs, 11 reservoir vessels
12 pipelines, 13 cooling and cleaning equipments
14 assemblies, 15 pipelines
16 shuntings, 17 shuntings
18 pipelines, 19 pipelines
20 modulating valve, 21 valve casings
22 valve pistons, 23 actuation surfaces
24 actuation surfaces, 25 valve springs
26 fluid spaces, 27 magnetic coils
28 armature A ports
B port C hole
I entrance O outlet
The S valve axis t endurance in cycle
D rotational speed L load
T temperature P
14Fluid supply pressure
V
14Volume flow P
20The valve actuation pressure
R
4Spin axis R
5Spin axis
Claims (31)
1. modulating valve of be used for regulating the delivery volume of rotary pump, described modulating valve comprises:
A) valve casing (21);
B) valve piston (22) is installed to be it can be moved in described valve casing (21), and comprises two actuation surfaces (23,24) for the valve actuation pressure (P20) of fluid;
C) valve spring (25), opposing is applied to power on the described valve piston (22) by described valve actuation pressure (P20); And
D) regulating equipment (27,28), by this regulating equipment, described valve piston (22) can be on the direction of the power that is applied by described valve actuation pressure (P20) or be conditioned by the opposite direction of described valve actuation pressure (P20) applied force,
Wherein, described two actuation surfaces (23,24) be configured to resist each other and be of different sizes, so that generation and described valve spring (25) act on the differential force on the described valve piston (22) on the contrary, and this differential force and described actuation surfaces (23,24) size difference is corresponding, and
The fluid space (26) that described two actuation surfaces (23,24) restrictions is identical and on the movable direction of described valve piston (22) toward each other.
2. modulating valve according to claim 1 is characterized in that, has at least one in the following characteristics:
-described regulating equipment (27,28) is electrically actuatable;
-described regulating equipment (27,28) is formed the magnetic regulating equipment;
-described regulating equipment (27,28) is resisted the power of described valve spring (25).
3. modulating valve according to claim 1 is characterized in that, has at least one in the following characteristics:
-described modulating valve (20) is Proportional valve;
-described modulating valve (20) is controlled or is adjusted by modulating pulse;
-described modulating valve (20) be Current Control or electric current is adjusted;
-described modulating valve (20) is voltage-controlled or voltage is adjusted;
-described modulating valve (20) comprise at least three ports for fluid (I, O, A, B);
-described modulating valve (20) can be changed between at least two dislocation;
-described modulating valve (20) is port valve.
4. modulating valve according to claim 1 is characterized in that, comprising:
-control apparatus or adjustment equipment, the volume flow (V14) that is used for control or adjusts the fluid supply pressure (P14) that will be produced by described rotary pump or will be carried by described rotary pump; And
-nominal value presets part, is used for pre-determining at least one pressure nominal value or volume flow nominal value;
-wherein, described control apparatus or adjustment equipment are according to described nominal value control or adjust described regulating equipment (27,28).
5. modulating valve according to claim 4 is characterized in that, described nominal value changes in predetermined mode.
6. modulating valve according to claim 1 is characterized in that, comprising:
-adjustment equipment, being used for adjusting will be by the fluid supply pressure (P14) of described rotary pump generation;
-nominal value presets part, is used for pre-determining the nominal value of fluid supply pressure (P14); And
-sensor is for the actual value of surveying described fluid supply pressure (P14);
-wherein, described adjustment equipment is with described actual value and described nominal value compares and control described regulating equipment (27,28) according to result relatively.
7. modulating valve according to claim 6 is characterized in that, described nominal value changes in predetermined mode.
8. according to claim 4 or 5 described modulating valve, it is characterized in that, comprise calibration equipment, by this calibration equipment, described modulating valve (20) can become adjustment described fluid supply pressure (P14) or described volume flow (V14) from controlling described fluid supply pressure (P14) or described volume flow (V14).
9. according to claim 6 or 7 described modulating valve, it is characterized in that, comprise calibration equipment, by this calibration equipment, described modulating valve (20) can become adjustment described fluid supply pressure (P14) from controlling described fluid supply pressure (P14).
10. modulating valve according to claim 1, it is characterized in that, described valve spring (25) is biased and applies bias force at described valve piston (22), described bias force is greater than being applied to power on the described valve piston (22) by the valve actuation pressure (P20) of maximum when described regulating equipment (27, the 28) proper functioning.
11. modulating valve according to claim 1 is characterized in that, described valve piston (22) can move forward and backward between a primary importance and a second place; On the primary importance of described valve piston (22), lead to described fluid space (26) for generation of entrance (I) and the port (A) of the pressure fluid of described valve actuation pressure (P20); And on the described second place, described valve piston (22) is separated described port (A) and the described entrance (I) that still leads to described fluid space (26).
12. modulating valve according to claim 1 is characterized in that, described valve casing (21) comprises entrance (I), first port (A) and second port (B) for pressure fluid; Described valve piston (22) can move forward and backward between a primary importance and a second place; And when described valve piston (22) is positioned on the described primary importance, described entrance (I) is connected to described first port (A) and separates with described second port (B), and when described valve piston (22) is positioned on the described second place, described entrance (I) is connected to described second port (B) and separates with described first port (A), in order to selectively pressure fluid is guided to described pump via described first port (A) or via described second port (B).
13. a rotary pump, it has adjustable delivery volume, and comprises:
A) pump case (1);
B) conveying chamber is formed in the described pump case (1), and is included in the fluid input (2) of the low voltage side of pump and at the on high-tension side fluid output (3) of pump;
C) delivery element (5) can move in described conveying chamber, for delivery of fluid; And
D) according to each is described for modulating valve (20) of regulating delivery volume among the claim 1-12, this modulating valve is arranged in the flowing of the fluid carried by described delivery element (5).
14. rotary pump according to claim 13 is characterized in that,
-actuation element (6,7) is set to movably is used for regulating the delivery volume in the described pump case (1) towards the positive of described delivery element (5) or around described delivery element;
-described actuation element (6,7) can bear actuation force on its movement direction, and described actuation force depends on the demand of the assembly (14) that will be supplied fluid;
-wherein said actuation element (6,7) and described delivery element (5) be regulon (5,6,7) part in, described regulon can be done as a whole seesawing in pump case (1), perhaps in actuation element and the described delivery element can be conditioned with respect to another and with respect to described pump case.
15. rotary pump according to claim 14 is characterized in that, described delivery element (5) rotates thereby make it can center on running shaft (R5) for being arranged on the conveying solid of rotation in the described conveying chamber.
16. according to claim 14 or 15 described rotary pumps, it is characterized in that, be provided with pump spring (10) to resist described actuation force.
17. rotary pump according to claim 14 is characterized in that, described actuation element (6,7) can bear the on high-tension side fluid of described pump, in order to produce described actuation force.
18. rotary pump according to claim 17 is characterized in that, described actuation element (6,7) forms the two-way function power piston, and this two-way function power piston comprises the first piston surface and dorsad and away from second piston face on described first piston surface; Pressure fluid can be born via first port (A) of described modulating valve (20) in described first piston surface, and described second piston face can bear pressure fluid via second port (B) of described modulating valve (20); And described valve piston (22) can move forward and backward between a primary importance and a second place; Wherein, on the primary importance of described valve piston (22), described modulating valve (20) only guides to pressure fluid described first piston surface, and on the second place of described valve piston (22), described modulating valve (20) only guides to pressure fluid described second piston face.
19. rotary pump according to claim 18 is characterized in that, described pressure fluid is the on high-tension side fluid of described pump.
20. positive displacement pump according to claim 14 is characterized in that, described actuation element (6,7) can axially or laterally move with respect to described spin axis (R5) with described delivery element (5) or with respect to described delivery element (5).
21. rotary pump according to claim 20 is characterized in that, described delivery element (5) is conveying with another delivery element (4) of described rotary pump and engages, in order to carry fluid.
22. rotary pump according to claim 21 is characterized in that, described actuation element (6,7) comprises first power piston (6) and second power piston (7); Described delivery element (5) is at described power piston (6,7) axially arrange between, and its can with described power piston (6,7) together as regulon (5,6,7) under the state of carrying joint, move forward and backward with respect to another delivery element (4).
23. rotary pump according to claim 13 is characterized in that, described pump is external gear pump or internal gear pump.
24. rotary pump according to claim 14 is characterized in that, described actuation element is the actuating ring around described delivery element, and described actuating ring can be mobile in a lateral direction with respect to the spin axis of described delivery element.
25. rotary pump according to claim 24 is characterized in that, described pump is wing pump, swing type shuttle block pump or internal gear pump.
26. rotary pump according to claim 13 is characterized in that, the fluid of being carried by described rotary pump is branched in the high pressure side of this pump, and this fluid is back to described pump via described modulating valve (20), in order to produce described actuation force in pump.
27. rotary pump according to claim 26 is characterized in that, the fluid that described rotary pump is carried is branched in the downstream of cleaning equipment (13).
28., it is characterized in that the described fluid that is refluxed produces described valve actuation pressure (P20) according to claim 26 or 27 described rotary pumps.
29. rotary pump according to claim 28 is characterized in that, comprising:
-detection facility, and the physical descriptor of the fluid demand of the assembly (14) that will be supplied by described pump for detection of at least one description (T, D, L);
-nominal value presets part, according to described at least one detected physical descriptor (T, D, L), the nominal value of the nominal value of the volume flow that formation will be transferred (V14) or the mobile supply pressure (P14) that will be produced by described rotary pump; And
-control apparatus or adjustment equipment are according to the control of described nominal value or adjust the regulating equipment (27,28) of described modulating valve (20).
30. rotary pump according to claim 29, it is characterized in that, comprise the sensor for the actual value of surveying described volume flow (V14) or described fluid supply pressure (P14), wherein said adjustment equipment is according to the actuating variable of the regulating equipment that relatively is formed for described modulating valve (20) (27,28) between described nominal value and the described actual value.
31. rotary pump according to claim 13 is characterized in that, has in the following feature at least one:
-described pump is used as being used for to internal-combustion engine (14) supplying lubricating oil or to the lubricating pump of automatic transmission sap pressure supply liquid in the vehicle;
-described pump is driven by described internal-combustion engine (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200810145866 CN101644259B (en) | 2008-08-07 | 2008-08-07 | Regulating valve used for regulating delivery volume of reciprocating pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200810145866 CN101644259B (en) | 2008-08-07 | 2008-08-07 | Regulating valve used for regulating delivery volume of reciprocating pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101644259A CN101644259A (en) | 2010-02-10 |
| CN101644259B true CN101644259B (en) | 2013-08-07 |
Family
ID=41656268
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200810145866 Active CN101644259B (en) | 2008-08-07 | 2008-08-07 | Regulating valve used for regulating delivery volume of reciprocating pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101644259B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017112700A1 (en) * | 2017-06-08 | 2018-12-13 | Schwäbische Hüttenwerke Automotive GmbH | control valve |
| CN110968121B (en) * | 2019-12-20 | 2023-06-20 | 西安文理学院 | Flow passively regulated intermediate device |
-
2008
- 2008-08-07 CN CN 200810145866 patent/CN101644259B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN101644259A (en) | 2010-02-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8523535B2 (en) | Adjusting valve for adjusting the delivery volume of a displacement pump | |
| KR100411834B1 (en) | A cylinder lubrication system for a multicylinder internal combustion engine | |
| DE69012403T2 (en) | Electro-hydraulic actuator. | |
| US8800399B2 (en) | Hydraulic circuit for automatic transmission having area controlled shift actuator valve with flow force compensation | |
| CN103591084B (en) | Temperature checking method in hydraulic means | |
| US10473100B2 (en) | Pump exhibiting an adjustable delivery volume | |
| US20030196618A1 (en) | Externally mounted DPCS (differential pressure control system) with position sensor control to reduce frictional and magnetic hysteresis | |
| CN101573527A (en) | Egr valve device | |
| CN102459965A (en) | Hydraulic valve for use in a control module of an automatic transmission | |
| CN102667261B (en) | The hydraulic transmission of braking can be improved | |
| US5927073A (en) | Electric hydraulic hybrid motor | |
| JP2013524102A (en) | Gear pump with continuously variable output flow rate | |
| US20200256336A1 (en) | Valveless hydraulic system | |
| CN101644259B (en) | Regulating valve used for regulating delivery volume of reciprocating pump | |
| KR20120006977A (en) | Direct control linear variable displacement vane pump | |
| RU2459982C2 (en) | Pressure control two-stage electrohydraulic mechanism | |
| CN101900143B (en) | Swing type hydraulic proportioning and servo valve | |
| EP3215746A1 (en) | Hydraulic pressure supply system | |
| CN103016466A (en) | Hydraulic oil supply unit, hydraulic pump station and oil supply control method of hydraulic oil supply unit | |
| CN107835886A (en) | There is the rotary piston pump of radial bearing on only one housing parts | |
| CN113227579A (en) | Adjustable screw pump | |
| US20090032746A1 (en) | Piezo-electric actuated valve | |
| CN109779690A (en) | The regulating device of axial piston machine | |
| RU2610364C2 (en) | Hydrostatic driving device | |
| CN102345600A (en) | Pressure pump with suction nut |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |