WO2009071264A1 - Système hydraulique muni d'une vanne à descente rapide réglable - Google Patents

Système hydraulique muni d'une vanne à descente rapide réglable Download PDF

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Publication number
WO2009071264A1
WO2009071264A1 PCT/EP2008/010200 EP2008010200W WO2009071264A1 WO 2009071264 A1 WO2009071264 A1 WO 2009071264A1 EP 2008010200 W EP2008010200 W EP 2008010200W WO 2009071264 A1 WO2009071264 A1 WO 2009071264A1
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WIPO (PCT)
Prior art keywords
valve
chamber
hydraulic
quick
pump
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.)
Ceased
Application number
PCT/EP2008/010200
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German (de)
English (en)
Inventor
Seppo Tikkanen
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of WO2009071264A1 publication Critical patent/WO2009071264A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/255—Flow control functions
    • 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
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a hydraulic system with a hydraulic actuator and at least one adjustable hydraulic pump.
  • the flow rates and thus e.g. the lifting and lowering speed are specified by the pump (s) in the system.
  • a gravitational force always acts on the boom of the bucket loader, that is, in the hydraulic system, for example, a load pressure always acts on a bottom side of the boom cylinder.
  • the lifting speed as well as the lowering speed is controlled by the flow rate on the bottom side of the cylinder.
  • the lowering speed should be 30% to 70% higher than the lifting speed to allow efficient operation of the machine.
  • a hydraulic system that allows a quick lowering function of a hydraulic cylinder.
  • the system includes a bypass valve located between the bottom of the hydraulic cylinder and the pump and connected directly to the tank.
  • the valve can be opened in the lowering operation of the cylinder and directs part of the volume flow directly into the tank.
  • the derived oil volume is therefore missing in the system and an additional pump is needed as a storage loading pump, which promotes the oil back into the circulation or into the storage tank, which requires additional energy.
  • a hydraulic system would be desirable that does not require an additional pump and in which the nominal size of the pump by the required operating speed against the load, for example when lifting a bucket or the pressing of garbage in refuse collection vehicles , is determined.
  • the aim of the present invention is therefore to achieve a higher speed in the load direction in a pump-controlled hydraulic working circle at the speed against the load direction predetermined nominal size of a hydraulic pump or vice versa to reduce the nominal size of the pump at the same lowering speed, without using an additional pump and thus to increase energy consumption in the system.
  • the invention relates to a hydraulic system having at least one hydraulic actuator, for example for lifting loads, comprising at least two chambers for moving the actuator in or against the load direction.
  • the chambers each have a connection for connection to the hydraulic system.
  • the hydraulic system comprises at least one adjustable hydraulic pump with at least two ports, one port being connected to a first chamber of the hydraulic actuator and the second port being connected to a second chamber of the hydraulic actuator.
  • the hydraulic system has at least one fast-flow valve with a controllable flow cross-section, via which both chambers can be connected.
  • the quick-lowering valve is arranged parallel to the pump and connects the two chambers of the actuator with each other, the quick-lowering valve is used as a by-pass circuit for the pump to increase the total volume flow and thus the operating speed. It is therefore possible to convey a portion of the pressure medium not by the pump, but by an existing pressure difference due to a load from the first chamber of the actuator directly into the second chamber of the actuator. Since in this case no longer the entire pressure medium must be pumped by the pump, but a part of the Pressure medium is pumped bypassing the pump through the quick-flow valve, it is possible to achieve an overall larger volume flow of the pressure medium. Accordingly, the quick-flow valve can be used to achieve, for example, a higher lowering speed when lowering the actuator. The increase in the operating speed is generally possible when the actuator is actuated in the load direction.
  • An advantage of the above-described design of the system is that, unlike conventional systems, there are no additional lines between the quick-release valve and a tank of the hydraulic system. In addition, can be dispensed with a feed pump that promotes pressure fluid from the tank back into the lines. Consequently, the energy consumption of the system can be reduced compared to other systems.
  • the quick-flow valve is opened only when the pump is fully swung out. This already creates a pressure difference between the chambers of the actuator before the opening of the quick-release valve.
  • the flow cross-section of the quick-release valve is dimensioned so that the setting of a pressure drop over the quick-flow valve is achieved. It is thus possible to pass a part of the volume flow through the quick-flow valve.
  • the flow cross section of the quick-release valve is preferably freely adjustable in a value range from 0% to 100%. It is therefore possible to influence the volume of oil delivered by the quick-flow valve or the volume flow with the aid of the adjustment of the flow cross-section.
  • the lowering speed or operating speed in the load direction of the actuator can thus be adapted individually to the wishes of a user. With the system described above, different speeds of the actuator can be achieved, depending on whether and how far the fast-flow valve is opened.
  • the pump delivers the same maximum oil volume when lifting or lowering the actuator, regardless of whether the quick-lowering valve is open or not. It is therefore possible to operate the pump in both modes of the actuator, in the lifting as well as in the lowering operation close to their optimum efficiency.
  • the quick-flow valve is closed, whereby a by-pass circuit of the actuator or the pump is prevented.
  • the entire pressure medium to be pumped is conveyed only with the help of the pump in one of the chambers.
  • the pump of the hydraulic system described above is preferably a dual-circuit pump and has a nominal size, which is designed according to the required speed against the load, that is, for example, the stroke speed of the actuator.
  • the pump is smaller and cheaper than when dimensioning the pump according to the required speed in the load direction, ie the lowering speed, which is generally above the required lifting speed.
  • the hydraulic system according to the invention also has a flow compensating valve, via which the first or the second chamber of the actuator can be connected to a tank volume, preferably via a pressure limiting valve.
  • the quantity compensation valve is designed such that an excess of pressure medium in one of the chambers of the actuator or in one of the lines connecting the chambers of the actuator to the pump is prevented during operation of the quick-release valve. This prevents pressure equalization between the two chambers of the actuator and thus ensures the function of the quick-release valve.
  • the present invention describes a method of actuating a hydraulic actuator by means of a hydraulic system.
  • a volume flow is generated from a first chamber of the hydraulic actuator into a second chamber of the hydraulic actuator by a pump.
  • the volume flow is increased to further increase the speed by opening a fast scavenge valve connecting the first to the second chamber.
  • the erfindunstrae method has the advantage that no longer the entire required for lowering a load volume flow from the first chamber must be funded in the second chamber by the pump. Rather, a portion of the total volume flow is conveyed via the quick-flow valve directly from the first chamber into the second chamber. Accordingly, the pump can be made smaller.
  • the movement of the actuator in the load direction is divided into two areas.
  • the user preferably selects from two control ranges, wherein the controllable fast-flow control valve can be opened in at least one of the two control ranges.
  • the user thus has the choice between the first control range, in which the conveying speed of the pump can be adjusted continuously, and a second control range, in that the fast-flow control valve can be actuated at the maximum delivery rate of the pump.
  • the pump already delivers maximum when opening the quick-release valve and thus has already set a pressure gradient between the two chambers of the actuator.
  • a user thereby has the choice of having the actuator lowered only by means of the pump or additionally adding the quick-flow valve for a faster lowering of the actuator.
  • the user can also adjust the speed of the pump continuously.
  • the quick-lowering valve can not be opened during this movement.
  • the quick-lowering valve is automatically closed in the lowering operation, if the load pressure exceeds a certain limit. It can thus be prevented that, for example, a machine boom under load during quick lowering operation represents a danger to the user or bystanders.
  • an overpressure in one of the two chambers of the actuator can be prevented by a quantity compensation valve integrated in the hydraulic system. This compensates for an excessive pressure medium flow generated by the hydraulic pump. The resulting difference quantity is discharged via the flow compensating valve into the tank.
  • FIG. 1 is a schematic representation of the hydraulic system according to the invention according to a preferred embodiment
  • Fig. 3 is a schematic representation of the hydraulic quick-release valve according to the invention with float valve
  • FIG. 4 shows a schematic representation of the hydraulic system according to the invention with a quantity compensation valve and discharge of the pressure medium via a pressure-limiting valve of the feed device, and
  • Fig. 5 is a schematic representation of the hydraulic system according to the invention with a flow compensating valve and separate pressure relief valve.
  • the actuator 1 has an actuator 1 with two chambers a and b. Further the actuator consists of a piston rod Ia and a piston Ib. The separation of the two chambers a, b is carried out by the piston Ib.
  • the second chamber b is arranged on a piston rod side of the actuator 1 and the first chamber a is arranged on the bottom side of the piston 1 b of the actuator 1.
  • a lifting and lowering of a load is assumed.
  • the hydraulic actuator can be actuated counter to a load direction, which corresponds to the lifting, or can be actuated in the load direction, which is the case when lowering.
  • This can be the case, for example, in a waste compactor, where work is performed against the load direction when compacting the refuse. It is assumed that for actuation against the load direction pressure medium of the first chamber a is supplied.
  • a pump 2 which is driven by a motor 3, preferably a diesel engine.
  • the pump 2 is designed to be adjustable in terms of its stroke volume and preferably a hydraulic axial piston machine in swash plate construction, which is pivotable from a neutral position in two directions. The stroke volume is adjusted by tilting the swashplate.
  • the pump 2 is a dual-circuit pump.
  • the dual-circuit pump has two individual pumps 2a, 2b.
  • the first individual pump 2 a is connected via a storage line 15 to a hydraulic accumulator 4. With its second connection, the first individual pump 2a is connected to a first actuating pressure line 16, which connects the first individual pump 2a to the first chamber a.
  • the second individual pump 2b also has two connections. A first connection is connected via a connecting line, which opens out in the first control pressure line 16 with the first chamber a. By contrast, the second connection of the second individual pump 2b is connected to the second chamber b via a second control pressure line 17.
  • the first control pressure line 16 and the second control pressure line 17 are connected to each other via a first connecting line 18.
  • a quick-flow valve 7 is arranged so that a throttled connection between the first control pressure line 16 and the second control pressure line 17 is produced in dependence on the setting of the quick-lowering valve 7.
  • a second connecting line 19 is formed, which connects the first actuating pressure line 16 with the second actuating pressure line 17.
  • two oppositely arranged check valves Vl and V2 are provided. Between these two check valves Vl, V2, which respectively open in the direction of the first actuating pressure line 16 to the second actuating pressure line 17, opens a feed pressure line 20 in the second connecting line 19.
  • the remote from the second connecting line 19 end of the feed pressure line 20 is connected to a feed pump 6.
  • the feed pump 6 sucks from a tank volume 5 Pressure medium via a suction line 21 at.
  • the feed pressure line 20 can be connected via a pressure limiting valve 11 to the tank volume.
  • the feed pump 6 is also driven by a drive shaft connected to the pump 2 motor 3.
  • the valves V 1 and V 2 are check valves which permit a flow only in the conveying direction of the pump 6 and thus make it possible to supply pressure medium in the event of pressure medium leakage.
  • the first control pressure line 16 is connected to the connecting lines 18 and 19.
  • the second actuating pressure line B is connected to the respective other ends of the connecting lines 18 and 19.
  • the hydraulic actuator 1 and arranged in the first connection line fast-lowering valve 7 are connected in parallel.
  • the pump 2 conveys pressure medium into the first actuating pressure line 16.
  • the rapid-flow control valve 7 is closed in the lifting mode.
  • the pressure medium passes into the first chamber a of the actuator 1.
  • b is conveyed from the second chamber to the pump 2. The result is a lifting or extension of the piston Ib of the actuator.
  • 6 pressure fluid can be provided from the tank with the help of the feed pump to compensate for pressure medium leakage.
  • the pump 2 delivers pressure medium from the first chamber a of the actuator 1 and into the second chamber b. Because of the piston rod Ia are the Volume flows from / into the first chamber a and in / out of the second chamber b different. The resulting difference volume is promoted by increasing the potential energy in the hydraulic accumulator 4. The result is a lowering or retraction of the actuator 1. Since it can come between the removal of pressure fluid from the hydraulic accumulator 4 and the return to a volume difference, as can be seen from the example below, is a way to charge the hydraulic accumulator 4 provided. This could be done for example by the feed pump 6, which would then be connected via a check valve to the hydraulic accumulator 4.
  • the quick-lowering valve 7 In order to increase the lowering speed, the quick-lowering valve 7 is provided.
  • the quick-flow valve 7 creates a throttled connection between the first control pressure line 16 and the second control pressure line 17.
  • the volumetric flow which is conveyed from the first chamber a into the second chamber b due to the pump pivot angle, it can thus be achieved with at least partially opened rapid-flow valve 7 pressure medium from the first chamber a flow bypassing the hydraulic pump 2 into the second chamber b.
  • the total volume flow from the first chamber a into the second chamber b thus increases, as a result of which the lowering speed is likewise increased.
  • the quick-lowering valve is, for example, an adjustable 2/2-way valve with proportional control between two end positions.
  • a control signal proportional to a control signal is generated, which acts against the fast lowering valve 7 against a fast-lowering valve 7 acting in its closed position return spring.
  • a regulation of the quick-release valve 7 is designed such that the opening of the quick-release valve 7 by a user is possible only at maximum delivery rate of the pump 2.
  • a user can do that Pump volume of the pump 2 stepless select up to the maximum delivery volume.
  • the user can open and close the quick-flow valve 7 with maximum delivery of pressure medium by the pump 2 if necessary. Accordingly, an acceleration of the lowering operation is achieved, since in addition to the pump 2 pressure fluid from the chamber a is conveyed through the quick-flow valve 7.
  • the quick-flow valve 7 is equipped with a variable flow cross-section. A user can thus regulate the opening of the valve between 0 and 100% and thus influence the lowering speed of the actuator 1.
  • the control of the quick-release valve 7 is preferably carried out electromagnetically.
  • other control possibilities for the quick-flow valve 7 may be provided, as shown by way of example in FIG.
  • a limitation of the lowering speed can be provided, which prevents the opening of the quick-release valve 7 at a certain load pressure or brings an already opened fast-flow valve 7 back to its starting position, in which the first Connecting line 18 is interrupted.
  • an integrated pressure sensor can measure the load pressure, that is to say the pressure in the first chamber a of the actuator 1, and pass this on to a control unit of the hydraulic system. If the load pressure exceeds a predetermined limit value, the quick-release valve 7 closes automatically.
  • this limit value corresponds to 1.2 times the pressure level of the actuator operation without load.
  • FIG. 2 shows a preferred connection of the quick-release valve 7, which is located in the first connection line 18. It is in the illustrated embodiment, a 2/2-proportional valve.
  • the initial position which is set by a return spring 7b
  • the connection between the control pressure lines 16 and 17 is blocked.
  • a throttled flow through the quick-flow valve 7 is made possible.
  • pressure medium passes from the first control pressure line 16 to the second control pressure line 17.
  • the flow in the reverse direction is blocked in the reverse direction even when the quick-flow control valve 7 is open due to an integrated non-return valve function.
  • the pressure line 7a shown enables the above-mentioned safety function on hydrostatic way.
  • the load pressure is increased, the hydraulic force acting in addition to the spring force of the return spring 7b increases in the closing direction.
  • the opening force required for opening also increases, and at constant opening force, the quick-lowering valve 7 is automatically brought to a closed position.
  • a control valve 8 is connected to the quick-flow valve 7 through the pressure line 8a.
  • a pressure surface of the quick-release valve 7 is acted upon by the pressure line 8a with a hydrostatic control force against the force of the return spring 7b.
  • the control valve 8 is preferably a 3/2 proportional valve with electromagnetic control. With the help of an additional spring 8c, a starting position of the valve is fixed. In the initial position, which forms a first end position of the valve, the control valve 8 according to FIG. 2 is therefore connected to the tank 5. In this switching position thus no pressure fluid from the control valve 8 through the line 8 a is promoted to the quick-lowering valve 7 and the pressure surface of the quick-release valve 7 is relieved.
  • the control valve 8 is actuated with the aid of the electromagnet 8d connected thereto, the pressure line 8a is increasingly connected to a pressure medium source 8b as a function of the height of the control signal.
  • the promotion of pressure medium from the source 8b may be realized for example by a feed pump. Since the control valve 8 is a proportional valve, different switching positions and thus also different flow rates can be realized by the control valve 8 with the aid of the control by the electromagnet 8d.
  • FIG. 3 shows an embodiment according to the invention of the quick-lowering valve 7 combined with an additional floating-position valve 9.
  • the floating-position valve 9 is arranged in the second connecting line 19.
  • the illustrated float valve 9 is 2/2-way valve.
  • the swimming pool is Positioning valve 9 locked. This starting position of the valve is determined by the spring 9a.
  • a second pressure line 9b is provided, which connects the floating position valve 9 with the first connection line 18 on the side of the quick-release valve 7 directed to the first chamber a.
  • the spring force of the spring 9a and the force of the pressurization on the float valve 9 by the pressure in the line 9b add up.
  • the electromagnetic control of the float valve 9 is thereby overridden hydraulically at elevated load pressure.
  • the float position valve 9 thus goes into its closed position for safety reasons when the load pressure rises above a value that can be determined by the magnitude of the electromagnetic force.
  • the electromagnetic force is generated by an electromagnet 9c as a counterforce to the spring 9a and to pressurize through the line 9b.
  • an opening of the float valve 9 is effected. Due to the open switching position of the float valve 9, a floating position of the hydraulic system is realized with simultaneous opening of the quick-release valve 7.
  • the first connecting line 18 of the hydraulic system is connected to the tank 5 through a throttle circuit 10 on the side lying to the second chamber b with respect to the quick-flow valve 7.
  • the flow of pressure medium to the tank 5 is thus limited.
  • the throttle circuit 10 is designed with a check valve so that, if appropriate, pressure medium can be sucked from the tank 5, so that, for example, cavitation is prevented in the hydraulic system.
  • FIG. 4 shows an embodiment according to the invention of the hydraulic system according to FIG. 1 with a quantity compensation valve 23.
  • This is connected via a first connecting line 22a to the actuating pressure line 16 and thus to the first chamber a of the actuator 1.
  • the quantity compensating valve 23 is connected to the actuating pressure line 17 and thus to the second chamber b of the actuator 1.
  • the quantity compensation valve 23 is also connected to the feed system and thus connected via the pressure relief valve 11 to the tank 5.
  • the quantity compensation valve 23 is preferably a 3/3-way valve which is actuated by occurring pressure forces or pressure differences. Depending on the pressure conditions occurring on the piston and the bottom side of the actuator 1, either the first chamber a or the second chamber b is connected to the tank 5 via the pressure relief valve. At pressure equilibrium, the quantity compensation valve 23 is in its starting position.
  • the quantity compensation valve 23 shown in FIG. 4 is a 3/3-way valve. In the starting position, the flow compensating valve 23 is blocked and the connecting lines 22a and 22b are separated from each other and from the tank 5. Two pressure measuring lines 25a, 25b are connected to the control pressure lines 16 and 17, whereby in the case of an overpressure in one of the two control pressure lines 16,17 the valve 23 is activated. This is done in such a way that the actuating pressure line 16 is connected to the tank 5 via the pressure limiting valve 11 by an overpressure in the actuating pressure line 17. At an overpressure in the control pressure line 16, however, the control pressure line 17 is connected to the tank 5 via the pressure relief valve 11. Accordingly, oil volume can be removed from the control pressure line 16 or from the control pressure line 17 to the tank 5 by actuation of the quantity compensation valve 23.
  • the quantity compensation valve 23 is preferably activated when the ratio of the current fast lowering speed to the maximum speed of the actuator 1 (in operation without fast-flow valve) exceeds a factor K.
  • the factor K is calculated as follows:
  • A_st is the area of the rod side of the actuator 1 and A_bo is the area of the bottom side of the actuator 1.
  • the ratio of the quick lowering speed to the maximum speed of the actuator 1 is less than the previously defined factor K, less oil volume is conveyed from the rod side and thus from the first chamber a to the second chamber b than is needed in the second chamber b.
  • the delivered volume of the quick-release valve 7 and the pump 2 is not sufficient to cover the needs of the rod side (chamber b) of the actuator 1. Therefore, in this case, additional oil volume is conveyed to the chamber b by means of the feed pump 6.
  • the flow compensating valve 23 is not activated in this case.
  • the flow compensating valve 23 is activated by the line 25b, whereby an excess of oil volume is prevented by oil volume flows from the control pressure line 16 via the pressure relief valve 11 of the feed system directly to the tank 5. Accordingly, it can be prevented with the quantity compensation valve 23 according to the invention that the pressures on the bottom side and on the rod side of the actuator 1 during operation of the Schnellsenkventils 7 equalize and affect the operation of the Schnellsenkventils 7 negative.
  • centering springs may be provided, which are not shown in the drawing.
  • -> Surplus is forwarded through purge valve 23 via the pressure relief valve to the tank 5 shows a modified starting from the embodiment of FIG. 4 embodiment.
  • a separate pressure limiting valve 11 ' is provided here, which connects the quantity compensating valve 23 to the tank.
  • the function is essentially identical to the function already described for FIG. 4.
  • This embodiment is therefore preferred. It also allows the pressure relief valve 11 'with respect to the quantities flowing through and the set pressure to adjust the quantity compensation function, without having to compromise on other functions of the pressure relief valve, such as a pressure limit of the allowable feed pressure to accept.
  • a commonly existing pressure relief valve for limiting the feed pressure of a feed system is not shown explicitly in FIG. 5. However, it is usually present as well. In rare exceptional cases, a direct connection of the quantity compensation valve 23 with the tank volume could be provided.

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

Abstract

L'invention concerne un système hydraulique qui présente un actionneur hydraulique (1), comprenant au moins une première chambre (a) et une deuxième chambre (b) munies respectivement d'un raccord pour être reliées au système hydraulique, et au moins une pompe hydraulique à cylindrée variable (2), comprenant au moins un premier raccord et un deuxième raccord. Selon l'invention, le premier raccord est relié avec la première chambre (a) de l'actionneur hydraulique et le deuxième raccord est relié avec la deuxième chambre (b) de l'actionneur hydraulique (1). La première chambre (a) est reliée avec la deuxième chambre (b) par le biais d'au moins une vanne à descente rapide (7) dont la section d'écoulement est réglable.
PCT/EP2008/010200 2007-12-04 2008-12-02 Système hydraulique muni d'une vanne à descente rapide réglable Ceased WO2009071264A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102007058337 2007-12-04
DE102007058337.2 2007-12-04
DE102008031007 2008-06-30
DE102008031007.7 2008-06-30
DE102008034301.3 2008-07-23
DE102008034301.3A DE102008034301B4 (de) 2007-12-04 2008-07-23 Hydraulisches System mit einem verstellbaren Schnellsenkventil

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WO2009071264A1 true WO2009071264A1 (fr) 2009-06-11

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CN102619817A (zh) * 2011-01-26 2012-08-01 南京工程学院 飞轮蓄能节能型液压振动系统
JP2015209943A (ja) * 2014-04-28 2015-11-24 日立建機株式会社 油圧駆動装置
US10392774B2 (en) 2017-10-30 2019-08-27 Deere & Company Position control system and method for an implement of a work vehicle
CN110552928A (zh) * 2019-09-24 2019-12-10 江苏徐工工程机械研究院有限公司 一种集成阀及浮动液压系统
CN115263839A (zh) * 2022-07-27 2022-11-01 江苏汇智高端工程机械创新中心有限公司 用于拖拉机提升系统的电液阀、拖拉机提升系统和拖拉机

Families Citing this family (3)

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WO2014176252A1 (fr) * 2013-04-22 2014-10-30 Parker-Hannifin Corporation Procédé d'augmentation de la vitesse d'un piston d'actionneur électro-hydrostatique
DE102013222165A1 (de) * 2013-10-01 2015-04-02 Deere & Company Frontladeranordnung
DE102014216031A1 (de) * 2014-08-13 2016-03-10 Robert Bosch Gmbh Hydrostatischer Antrieb und Ventilvorrichtung dafür

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EP1621777A2 (fr) * 2004-07-30 2006-02-01 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Entraînement linéaire hydraulique, en particulier actionneur hydraulique de transmission
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US20070166168A1 (en) * 2006-01-16 2007-07-19 Volvo Construction Equipment Ab Control system for a work machine and method for controlling a hydraulic cylinder in a work machine

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SE521308C2 (sv) 1999-12-27 2003-10-21 Bruun Ecomate Ab Mobil hanteringsanordning med hydraulkrets
JP2004190845A (ja) 2002-12-13 2004-07-08 Shin Caterpillar Mitsubishi Ltd 作業機械の駆動装置
DE10344480B3 (de) 2003-09-24 2005-06-16 Sauer-Danfoss Aps Hydraulische Ventilanordnung
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DE2538676A1 (de) * 1975-08-30 1977-03-03 Voegele Ag J Hydrostatischer fahrantrieb fuer fahrzeuge
EP0081703A1 (fr) * 1981-12-05 1983-06-22 Robert Bosch Gmbh Opérateur électrohydraulique
EP1621777A2 (fr) * 2004-07-30 2006-02-01 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Entraînement linéaire hydraulique, en particulier actionneur hydraulique de transmission
US20070079609A1 (en) * 2005-10-06 2007-04-12 Brinkman Jason L Hybrid hydraulic system and work machine using same
US20070166168A1 (en) * 2006-01-16 2007-07-19 Volvo Construction Equipment Ab Control system for a work machine and method for controlling a hydraulic cylinder in a work machine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102619817A (zh) * 2011-01-26 2012-08-01 南京工程学院 飞轮蓄能节能型液压振动系统
CN102619817B (zh) * 2011-01-26 2015-07-15 南京工程学院 飞轮蓄能节能型液压振动系统
JP2015209943A (ja) * 2014-04-28 2015-11-24 日立建機株式会社 油圧駆動装置
US10392774B2 (en) 2017-10-30 2019-08-27 Deere & Company Position control system and method for an implement of a work vehicle
CN110552928A (zh) * 2019-09-24 2019-12-10 江苏徐工工程机械研究院有限公司 一种集成阀及浮动液压系统
CN115263839A (zh) * 2022-07-27 2022-11-01 江苏汇智高端工程机械创新中心有限公司 用于拖拉机提升系统的电液阀、拖拉机提升系统和拖拉机

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DE102008034301B4 (de) 2019-02-14

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