CN106481607A - For two pumps and the control device of the hydraulic pressure of multiple actuators - Google Patents

For two pumps and the control device of the hydraulic pressure of multiple actuators Download PDF

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Publication number
CN106481607A
CN106481607A CN201610773990.1A CN201610773990A CN106481607A CN 106481607 A CN106481607 A CN 106481607A CN 201610773990 A CN201610773990 A CN 201610773990A CN 106481607 A CN106481607 A CN 106481607A
Authority
CN
China
Prior art keywords
pressure
pump
dividing plate
actuator
control device
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.)
Pending
Application number
CN201610773990.1A
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Chinese (zh)
Inventor
C.凯尔
F.里克霍夫
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of CN106481607A publication Critical patent/CN106481607A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F15B2211/41518—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve being connected to multiple pressure sources
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The present invention relates to the control device of hydraulic pressure, there is the first dividing plate that persistently can be adjusted, the first actuator for being conducted to arrange is able to by starting point through the first separator pressure fluid with the first and second pumps, at least one second partition that persistently can be adjusted is set, pressure fluid can be conducted to second actuator with the second pump as starting point through it, it is provided with the pressure balance of the 3rd dividing plate that persistently can be adjusted, storage tank can be conducted to as starting point with the first pump through the pressure balance pressure fluid, pressure balance is loaded towards the closing direction of the 3rd dividing plate by the first spring, it is poor that the pretension of the first spring defines first pressure.According to the present invention, first check-valve is connected between the first pump and at least one first dividing plate, the first check-valve only allows the fluid stream from the first pump to described at least one first dividing plates, 3rd dividing plate is connected between the first pump and check-valves, and the second pump is connected between check-valves and at least one first dividing plates.

Description

For two pumps and the control device of the hydraulic pressure of multiple actuators
Technical field
The present invention relates to a kind of control device of the hydraulic pressure according to the present invention and the hydraulic pressure with such control device Drive system.
Background technology
The drive system of the known hydraulic pressure with control device, the control device from 10 2,012 208 938 Al of DE Can for example use in wheel loader.It is provided with multiple first actuators and the second actuator.In addition, being provided with the first He Second pump, wherein, the first pump has constant discharge volume, and wherein, the second pump has the discharge volume that can be adjusted.As long as holding Few pressure fluid only accepted by row device, then the actuator is supplied by the second pump only, and this saves energy very much.Favourable in cost The first pump this is transported in storage tank with little back pressure.Only when the first actuator needs many pressure fluids, the first pump is Conveyed with high pressure.
Content of the invention
It is an advantage of the current invention that the volume flow in pressure balance importing storage tank is less.Especially, closed using middle position Close direction valve.In addition, control device is favourable especially in cost.Additionally, the being accurately controlled property of actuator is especially good.
According to it is proposed that, be connected to the first non-return between the first pump and at least one first dividing plate Valve, the first check-valve only allow the fluid stream from the first pump to described at least one first dividing plates, wherein, the 3rd dividing plate It is connected between the first pump and check-valves, wherein, the second pump is fluidly connected to check-valves and at least one first dividing plate Between.
Preferably, all of first dividing plate is fluidly connected in parallel to common branch part, wherein, unique first Check-valves is fluidly connected between branch part and the first pump.
By first or the second partition that persistently can adjust is adjusted, arranged first or the second actuator can be adjusted Movement velocity.First or second direction valve can be arranged respectively to the first or second actuator, can be adjusted using direction valve The direction of motion of the relevant actuator of section.First or the second partition that persistently can adjust and first or the second party that are arranged Preferably respectively jointly actuate to valve, wherein, they preferably are formed by common valve slider.Preferably, there are only One second partition.
Preferably, the control device of hydraulic pressure have the first and second pump joint positions, at least one storage tank joint area with And the first and second working joint positions for the first or second actuator, the system of their most preferably fluid lines Part.First pump preferably has constant discharge volume.The reason for for efficiency, the second pump preferably has can The discharge volume for persistently adjusting, wherein, second pump also can be with constant discharge volume.
Favourable modification and the evolutionary approach of the present invention is illustrated in preferred embodiment and other embodiments.
Can be provided that, arrange the first load pressure to each first dividing plate, the load pressure is depended on relevant The pressure in the downstream of the first dividing plate, wherein, the second load pressure depends on the pressure in the downstream of second partition, wherein, arranges Pump control mechanism, can adjust the second pump by adjusting the discharge volume of the second pump using the pump control mechanism to such value Transmission pressure, the value with second pressure set in advance difference be located at from pressure marshalling maximum pressure top, the pressure Power marshalling is formed by described at least one first load pressures and the second load pressure.Thus, the transmission pressure of the second pump be enough to All of first and second actuator is supplied using pressure fluid.First and second load pressures preferably connect in input side Cascade to reversal valve, wherein, the output section of reversal valve cascade is connected to pump control mechanism.First or second load pressure is preferably etc. In the pressure in the downstream of first for being arranged or second partition, as long as the flow of fluid for being arranged is not cut off.When being carried When the flow of fluid for arriving is ended, relevant load pressure is preferably equivalent to the pressure in storage tank.Through this, when actuator at least it One static when, just save energy.
Can be provided that, second pressure difference is poor more than first pressure.Thus, the transmission pressure of the second pump is more than the first pump Transmission pressure, as long as the transmitting stream of the maximum of the second pump be enough to supply all of actuator using pressure fluid.First stops Return valve the second pump transmission pressure this running status in be forced in closed position, wherein, the first pump whole Transmitting stream is through pressure balance with little back pressure stream in storage tank.Thus, all of actuator is saved energy ground and can be adjusted The second pump supplied using pressure fluid.
Can be provided that, pressure balance is carried out freely at least one first load pressure along the closing direction of the 3rd dividing plate The pressure-loaded of the maximum of the pressure marshalling that power is formed.Thus in the pressure marshalling being previously mentioned comprising the second actuator the Two load pressures, because the second actuator is only supplied using pressure fluid by the second pump.The second especially high load pressure Thus power do not cause the energy loss at the first pump.The pressure of the maximum that mentions afterwards is preferably at above-mentioned reversal valve cascade Take, namely take at the first controlling position.
Can be provided that, pressure balance along the 3rd dividing plate opening direction by pressure-loaded, the pressure is only applied to Return between valve and at least one first dividing plate.Preferably, the pressure being previously mentioned is the pressure at the above-mentioned branch part. Therefore, pressure balance indirectly adjusts the transmission pressure of the first pump, but adjusts in fact the pressure in the downstream of first check-valve Power.But, this pressure is equal to the transmission pressure of the second pump, as long as the transmit capacity of the pump be enough to supply using pressure fluid All of actuator.As long as first check-valve closure, then pressure balance by the pressure extrusion in position fully through opening, It is sent in the storage tank through pressure balance with especially little back pressure so as to the first pump.
The 4th dividing plate that persistently can be adjusted that can be adjusted jointly and persistently can adjust the can be provided with The pressure-gradient control valve of five dividing plates, wherein, the 4th dividing plate is opened in each position of the pressure-gradient control valve, wherein, the 5th dividing plate only when The pressure in the downstream of the 4th dividing plate is just opened when exceeding value set in advance, and wherein, the second pump is through the 4th dividing plate and the Two dividing plates are fluidly connected, and wherein, the second pump is fluidly connected with least one second partition through the 5th dividing plate.It is preferred that Ground, the second pump are connected with the branch part through the 5th dividing plate.If the transmitting stream of the second pump no longer be enough to utilize pressure current Body supplying all of actuator, then the 5th dividing plate closure, so as to the second actuator only by the second pump using pressure fluid come Supply.It is accomplished that through this, the second actuator is sufficiently supplied using pressure fluid in each running status, and specifically For do not rely on：The mode that first actuator is steered.
Can be provided that, the pressure-gradient control valve along the 5th dividing plate closing direction by second spring and by second load Pressure-loaded, wherein, it along the 5th dividing plate opening direction by the pressure-loaded in the downstream of the 4th dividing plate.Through this, described Pressure-gradient control valve can utilize pressure in the downstream of the first dividing plate to load in a straightforward manner.When the second actuator does not move, Second load pressure is preferably coupled to the storage tank, and wherein, it is connected to the pressure in the downstream of second partition in remaining situation Power.Through this, the transmitting stream of the second pump also can be used for supplying the first actuator when following, i.e., when the first actuator is static When, wherein, the power of big outside is acted at the actuator.
Additionally, making every effort to protection with the first and second pumps and at least one first actuators and the second actuator（They Fluidly it is connected with each other through the control device of the hydraulic pressure according to the present invention）Hydraulic pressure drive system, wherein, the first pump has Constant discharge volume, wherein, the second pump has the discharge volume that persistently can be adjusted.
Can be provided that, the first and second pumps be in the rotation drive connection of common motor in.Motor preferably refers to Be internal combustion engine, preferably refer to diesel motor.
Additionally, making every effort to the mobile work machines of the drive system of the hydraulic pressure of the with good grounds present invention of protection band, wherein, second holds Row device and second partition are the parts of the control unit of mobile work machines, wherein, described at least one first dividing plates and institute The first actuator for arranging is the part of the working solution splenium of mobile work machines.Mobile work machines for example can refer to It is excavator, wheel loader, agricultural traction engine or commuting vehicle.
Obviously, feature above-mentioned and next also to be explained can not only be used in the combination for correspondingly illustrating In, could be used that in other combinations or be used alone, without deviating from the framework of the present invention.
Description of the drawings
Next the present invention is explained in detail by accompanying drawing.In accompanying drawing：
Fig. 1 is the drive system of the hydraulic pressure of the control device with the with good grounds present invention.
Specific embodiment
Fig. 1 shows the drive system 10 of the hydraulic pressure of the control device 20 with the with good grounds present invention.Control device 20 has First pump joint position 70, the first pump 11 with constant discharge volume are connected to the pump joint position.First pump 11 is from storage Suction pressure fluid and pass it through the first pump joint position 70 and transmitted parallel to multiple first dividing plates 21 in case 15.Pressure Power fluid preferably refers to liquid, preferably refers to hydraulic oil.Storage tank mark shown in FIG refers to all of identical Storage tank 15.
The distribution that pressure fluid to the first different dividing plate 22 is carried out produces the branch of the corresponding system in fluid line At position 75.First check-valve 25 is constructed between the first pump joint position 70 and branch part 75, the first check-valve is only Solely allow from the 11 straight fluid stream towards the first dividing plate 21 of the first pump.
In addition, pressure balance 26 is provided with the 3rd dividing plate 28 that persistently can be adjusted.3rd dividing plate 28 is fluidly connected to Between one pump joint position 70 and first check-valve 25, so as to pressure fluid with the first pump 11 as starting point through the 3rd dividing plate 28 Can be transmitted in storage tank 15.Pressure balance 26 is connected with the storage tank joint area 72 of control device 20 for this, 15 fluid of storage tank Be connected to the storage tank joint area.Along the closing direction of the 3rd dividing plate 28, pressure balance 26 using the first spring 27 and Pressure at the first controlling position 76 is loading.The pretension of the first spring 27 defines the first pressure for being calculated as such as 5bar Difference.In the direction of the opening, pressure balance 26 is loaded using the pressure at branch part 75.Accordingly, 26 handle of pressure balance exists Pressure at branch part 75 is adjusted to such value, and the value is located at the pressure in the first controlling position 76 with first pressure difference Top.It is the load pressure of the maximum at the first actuator 13 in the pressure at the first controlling position 76, as long as the execution Device moves.
First actuator 13 for example refers to hydraulic cylinder or hydraulic motor, and they are preferably encased mobile work machines, example In the working solution splenium of excavator, wheel loader, agricultural traction engine or commuting vehicle.First actuator 13 is all through first With the second working joint position 73；74 are fluidly connected to control device 20.Arrange for each first actuator 13 and can continue The first dividing plate 21 for adjusting and first direction valve 23.The motion of the first arranged actuator 13 is set using the first dividing plate 21 Speed, wherein, sets its direction of motion using first direction valve 23.
In a first direction in the first working position of valve 23, by pressure fluid from branch part 75 through the first dividing plate 21 to The first arranged working joint 72 to conduct, wherein, pressure fluid is transmitted to storage tank 15 from the second relevant working joint 74 In.First working joint position, 73 here is fluidly connected with the load report position 45 at valve 23 in a first direction.First In second working position of direction valve 23, by pressure fluid from branch part 75 through the first dividing plate 21 towards second for being arranged Working joint 74 conducts, and wherein, pressure fluid is transmitted in storage tank 15 from the first relevant working joint 73.Second working joint 74 here of position is fluidly connected with the load report position 45 at valve 23 in a first direction.In the sequestration site at middle part, bear Carry report position 45 to be connected with storage tank 15, wherein, remaining fluid flow path all of is cut off.Thus, when relevant When one actuator 13 moves, it is applied at load report position 45 in the pressure in the downstream of the first dividing plate 21, as long as this first is held Row device is static, then be applied at load report position 45 in the pressure in storage tank 15, and the pressure is substantially calculated as zero.First direction Valve 23 is extruded towards the direction of sequestration site preferably by least one spring.First dividing plate 21 and first direction valve 23 preferred Can jointly adjust, wherein, they preferably are formed by common valve slider.Same situation is applied to second partition 22 and second direction valve 24.
Second check-valve 29 is preferably arranged to each first dividing plate 21, the second check-valve is only allowed from branch The straight fluid stream towards the first dividing plate 21 in position 75.
The load report position 45 of first direction valve 23 respectively input side be connected to arranged for reversal valve cascade 40 Part the first reversal valve 41.The first controlling position 76 that has discussed defines the output section of reversal valve cascade 40, The reversal valve cascade includes all of first reversal valve 41.Therefore the maximum of all of first actuator 13 is there applied with Load pressure, as long as this first actuator motions.The first reversal valve 41 being located at in the first position in reversal valve cascade 40 Free input unit be preferably coupled to storage tank 15.Certainly he can also be connected to load report position 45, so as to give this One reversal valve 41 arranges two load report positions 45.
To the second actuator 14 arrange second direction valve 24 identical with first direction valve 23 build, so as to relevant with this Ground is with reference to above-mentioned embodiment.Same situation is applied to the first and second dividing plates 21；22.Second actuator 14 is referred preferably to Be hydraulic cylinder, the part of the control unit of the mobile work machines that the hydraulic cylinder has most preferably been discussed.Second Furthermore actuator 14 is by the first and second working joint positions 73；74 are connected to the control device 20.
The second reversal valve 42, the load report position 45 of second direction valve 24 and the first control are arranged to second direction valve 24 Position processed 76 is connected at second reversal valve in input side.Corresponding to this, all of first and second reversal valve 41；42 combinations It is connected as reversal valve cascade 40.The output section of the second reversal valve 42 defines the second controlling position 77, and all of first and second Actuator 13；The load pressure of 14 maximum is applied at the controlling position, as long as these actuator motions.
Second pump 12 has the discharge volume that can be adjusted, and wherein, second pump is fluidly connected to control device 20 Second pump joint position 71.Second pump 12 also can be with constant discharge volume, and wherein, then pump control mechanism 60 is configured to pressure Power balance, the pressure balance are transmitted to superfluous volume flow in storage tank 15.Second pump 12 is together with the first pump 11 by common Motor 16, preferably internal combustion engine, preferred ground diesel motor are driving.It extracts pressure fluid and should from storage tank 15 Pressure fluid is sent to pressure-gradient control valve 50 under stress.Pressure-gradient control valve 50 is facilitated, and first and foremost the second actuator 14 is by the second pump 12 Supplied using pressure fluid.Only the more pressure fluids that takes at the second actuator 14 are compared when the second pump 12 is transferred When, the pressure fluid is flowed towards the first actuator 13 through branch part 75.
Pressure-gradient control valve 50 has the 4th dividing plate and single 5th dividing plate 51 that jointly persistently can be adjusted；52.4th every Plate 51 is opened at least in part with regard to the whole regulation stroke of pressure-gradient control valve 50.Differently, the 5th dividing plate 52 has and fully closes The terminal region of conjunction.Pressure fluid can（With the second pump 12 as starting point through the 4th dividing plate 51）In addition through persistently adjusting The second partition 22 of section, in addition flow towards the second actuator 14 through second direction valve 24.Additionally, pressure fluid can be from Two pumps 12 are flowed towards branch part 75 through the 5th dividing plate 52.On the closing direction of the 5th dividing plate 52, using in the second bullet Pressure at the load report position 45 of spring 53 and second direction valve 24 is loading pressure-gradient control valve 50.The side of opening in the 5th dividing plate 52 Upwards, using pressure-gradient control valve 50 described in the pressure-loaded in the upstream of second partition 22.Pressure-gradient control valve is thus at second partition 22 Pressure drop adjust to the pressure equivalent of second spring 53.If the transmitting stream of the second pump 12 is not enough to be maintained this pressure differential, Then the 5th dividing plate 52 is fully closed, and is supplied using pressure fluid so as to the second actuator 14 only.
Pump control mechanism 60 is arranged to the second pump 12, the pump control mechanism is by the transmission pressure 62 of the second pump 12 by adjusting second The discharge volume of pump and be adjusted in such value, the value with second pressure set in advance difference be located in the second controlling position 77 The top of the pressure at place.Second pressure difference is for example calculated as 15bar, and wherein, it is more than by the first bullet at pressure balance 26 The first pressure that spring 27 is defined is poor.Thus, the transmission pressure of the second pump 12 is more than the transmission pressure of the first pump 11, as long as the second pump The transmitting stream of 12 maximum be enough to supply all of actuator 13 using pressure fluid；14.
Therefore, the transmission pressure 62 of the second pump 12 extrudes first check-valve 25 to closed position, wherein, the first pump 12 whole transmitting stream is flowed in storage tank 15 through the 3rd dividing plate 28 of pressure balance 26.Here, pressure balance 26 is by branch Pressure at position 75 is adjusted in position fully through opening, so as to only there is little pressure drop at the 3rd dividing plate 28, So as to only produce little energy loss.There is this running status, when one or more first actuators 13 lentamente move, when This first actuator thus in precise control region run when.
If by actuator 13；14 have taken the more pressure fluids that can be transmitted than the second pump 12, then in pressure-gradient control valve The 5th dividing plate 52 at 50 is closed.Thus, pressure balance 26 is the transmission pressure of the first pump 11 or at branch part 75 Pressure is adjusted to such value, and the value is located at the pressure in the first controlling position 76 with first pressure difference（Namely all of The load pressure of the maximum of one actuator 13）Top.First pressure difference is by the pressure for being for example calculated as 5bar of the first spring 27 Equivalent is defined.Second pump 12 is only transmitted towards the second actuator 14 in this running status.
It should be appreciated that pressure limit valve 61, which is connected to branch part 75.If the pressure at this exceedes set in advance Fixed limiting value, then pressure fluid flow in storage tank 15 from branch part 75, so as to the pressure at branch part 75 again Decline.
It should be noted that first and/or second direction valve 23；24 can also be configured to middle position opens valve.Replace cut-off portion Position, is then present around position, and the cincture position is defined around passage, and only little volume flow is flowed in the cincture position Dynamic, the volume flow is used for adjusting the second pump 12.
Reference list
The drive system of 10 hydraulic pressure
11 first pumps
12 second pumps
13 first actuators
14 second actuators
15 storage tanks
16 motors
The control device of 20 hydraulic pressure
21 first dividing plates
22 second partitions
23 first direction valves
24 second direction valves
25 first check-valves
26 pressure balance
27 first springs
28 （Pressure balance）3rd dividing plate
29 second check-valves
40 reversal valves are cascaded
41 first reversal valves
42 second reversal valves
43 first load pressures
44 second load pressures
45 load report positions
50 pressure-gradient control valves
51 the 4th dividing plates
52 the 5th dividing plates
53 second springs
60 pump control mechanisms
61 pressure limit valves
The transmission pressure of 62 second pumps
70 first pump joint positions
71 second pump joint positions
72 storage tank joint areas
73 first working joint positions
74 second working joint positions
75 branch parts
76 first controlling positions
77 second controlling positions

Claims (10)

1. it is used for and the first pump and the second pump（11； 12）, at least one first actuators（13）With the second actuator（14）Carry out The control device of the hydraulic pressure for using（20）, wherein, control device（20）There is the first dividing plate that persistently can be adjusted（21）, pass through First dividing plate causes pressure fluid with the first pump and the second pump（11；12）Arrange first can be all conducted to by starting point to hold Row device（13）, wherein, at least one second partition that persistently can be adjusted is set（22）, pressure current is caused through the second partition Body is with the second pump（12）The second actuator for arranging can be conducted to by starting point（14）, wherein, it is provided with and persistently can adjusts 3rd dividing plate of section（28）Pressure balance（26）, pressure fluid is caused with the first pump through the 3rd dividing plate（11）For starting point energy Storage tank is enough conducted to（15）, wherein, pressure balance（26）By the first spring（27）Along the 3rd dividing plate（28）Closing direction add Carry, wherein, the first spring（27）Pretension define first pressure poor,
Characterized in that, in the first pump（11）With described at least one first dividing plates（21）Between be connected with first check-valve （25）, the first check-valve only allowed from the first pump（11）To described at least one first dividing plates（21）Fluid stream, its In, the 3rd dividing plate（28）It is connected to the first pump（11）And check-valves（25）Between, wherein, the second pump（12）It is fluidly connected to stop Return valve（25）With described at least one first dividing plates（21）Between.
2. according to the control device of the hydraulic pressure described in claim 1, wherein, each first dividing plate is given（21）Arrange the first load pressure Power（43）, the load pressure depended in the first relevant dividing plate（21）Downstream pressure, wherein, the second load pressure（44） Depend in second partition（22）Downstream pressure, wherein, be provided with pump control mechanism（60）, being passed through using the pump control mechanism will Second pump（12）Discharge volume adjust and can adjust the second pump to such value（12）Transmission pressure（62）, the value is with pre- The second pressure difference for first setting is located at the top of the pressure of the maximum from the marshalling of such pressure, and the pressure is organized into groups by least one Individual first load pressure（43）With the second load pressure（44）Formed.
3. according to the control device of the hydraulic pressure described in claim 2, wherein, second pressure difference is poor more than first pressure.
4. according to the control device of the hydraulic pressure described in Claims 2 or 3, wherein, pressure balance（26）Along the 3rd dividing plate（28） Closing direction carried out freely at least one first load pressures（43）The pressure-loaded of the maximum of the pressure marshalling of formation.
5. according to the control device of hydraulic pressure in any one of the preceding claims wherein, wherein, pressure balance（26）Along the 3rd Dividing plate（28）Opening direction by such pressure-loaded, the pressure is applied to check-valves（25）With described at least one first every Plate（21）Between.
6. according to the control device of hydraulic pressure in any one of the preceding claims wherein, wherein, it is provided with and can be adjusted jointly The 4th dividing plate that persistently can be adjusted of section（51）With the 5th dividing plate that persistently can be adjusted（52）Pressure-gradient control valve, wherein, the 4th Dividing plate（51）In the pressure-gradient control valve（50）Each position in open, wherein, the 5th dividing plate（52）Only when in the 4th dividing plate（51） Downstream pressure exceed value set in advance when just open, wherein, the second pump（12）Through the 4th dividing plate（51）With Two dividing plates（22）Fluidly it is connected, wherein, the second pump（12）Through the 5th dividing plate（52）With at least one second partition（22）Stream It is connected body.
7. according to claim 6, the control device of hydraulic pressure described in claim 2, wherein, the pressure-gradient control valve are quoted（50）Along 5th dividing plate（52）Closing direction by second spring（53）And by the second load pressure（44）Load, wherein, the pressure-gradient control valve Along the 5th dividing plate（52）Opening direction by the 4th dividing plate（51）Downstream pressure-loaded.
8. with through the control device by hydraulic pressure in any one of the preceding claims wherein（20）Fluidly it is connected with each other First pump and the second pump（11； 12）And at least one first actuators（13）With the second actuator（14）Hydraulic pressure driving System, wherein, the first pump（11）With constant discharge volume, wherein, the second pump（12）There is the discharge that persistently can be adjusted Volume.
9. according to the drive system of the hydraulic pressure described in claim 8, wherein, the first pump and the second pump（11； 12）Be in common Motor（16）Rotation drive connection in.
10. the mobile work machines of the drive system according to the hydraulic pressure described in claim 8 or 9, wherein, the second actuator are carried （14）And second partition（22）It is the part of the control unit of mobile work machines, wherein, described at least one first dividing plates （21）With the first actuator for being arranged（13）It is the part of the working solution splenium of the mobile work machines.
CN201610773990.1A 2015-09-02 2016-08-31 For two pumps and the control device of the hydraulic pressure of multiple actuators Pending CN106481607A (en)

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