EP2613058B1 - Hydraulic system - Google Patents

Hydraulic system Download PDF

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Publication number
EP2613058B1
EP2613058B1 EP12005536.3A EP12005536A EP2613058B1 EP 2613058 B1 EP2613058 B1 EP 2613058B1 EP 12005536 A EP12005536 A EP 12005536A EP 2613058 B1 EP2613058 B1 EP 2613058B1
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EP
European Patent Office
Prior art keywords
hydraulic
viscosity
pressure
piston
throttle
Prior art date
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Active
Application number
EP12005536.3A
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German (de)
English (en)
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EP2613058A3 (fr
EP2613058A2 (fr
Inventor
Andreas Kurzen
Pascal Progin
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.)
Liebherr Machines Bulle SA
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Liebherr Machines Bulle SA
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Publication of EP2613058A2 publication Critical patent/EP2613058A2/fr
Publication of EP2613058A3 publication Critical patent/EP2613058A3/fr
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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
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/045—Compensating for variations in viscosity or temperature
    • 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
    • F15B7/008—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors with rotary output
    • 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
    • F15B2211/2053—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
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/40—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • 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
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • 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
    • F15B2211/66—Temperature control methods
    • 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
    • F15B2211/7058—Rotary output members

Definitions

  • the present invention relates to a hydraulic system with a closed hydraulic circuit consisting of hydraulic pump and hydraulic motor, with a feed pump to compensate for volume losses in the closed circuit and with a flushing device for feeding out a part of the hydraulic fluid from the closed circuit.
  • the hydraulic pump conveys fluid and thus drives the hydraulic motor.
  • the amount of oil it exits is returned directly to the hydraulic pump.
  • the volumetric losses are compensated for by the feed pump.
  • the flushing device feeds part of the oil out of the circuit to avoid overheating.
  • flushing valves are usually used which are designed as constant systems and, from a certain pressure difference between the two sides of the hydraulic circuit, suddenly deliver a constant flow of feed fluid.
  • the DE 10 2010 006464 A1 shows a hydraulic system that has all the features from the preamble of claim 1. The same applies to the revelation of the DE 10 2005 051324 A1 .
  • the US 2010/095665 A1 shows a hydraulic system that has all the features from the preamble of claim 9.
  • the object of the present invention is to provide an improved flushing device for such a hydraulic system.
  • this object is achieved by a hydraulic system according to claim 1 or claim 9.
  • the hydraulic system according to the invention has, inter alia, a closed hydraulic circuit comprising a hydraulic pump and a hydraulic motor, a feed pump for compensating for volume losses in the closed circuit and a flushing device for feeding out part of the hydraulic fluid from the closed circuit.
  • the flushing device is designed in such a way that the outlet fluid flow depends on the temperature of the hydraulic fluid. The present invention thus allows a flushing of the hydraulic fluid in a closed circuit as required, and thus a more efficient operation of the hydraulic system.
  • the exit fluid flow is fed to a hydraulic cooler and / or the tank.
  • the outlet fluid flow increases as the temperature of the hydraulic fluid rises, so as to prevent overheating of the hydraulic fluid in a closed circuit as required.
  • the feed fluid flow can be correspondingly low.
  • the flushing device has a viscosity-dependent throttle.
  • the present invention takes advantage of the physical fact that the viscosity of the hydraulic fluid decreases with increasing temperature. This increases the flow through the viscosity-dependent throttle as the temperature of the hydraulic fluid rises.
  • the exit fluid flow is thus variable due to the use of a viscosity-dependent throttle, with a lot of exit fluid flow occurring in the case of hot oil, and the temperature in the closed circuit thus being reduced.
  • the use of a viscosity-dependent throttle has the further advantage that the exit fluid flow does not change abruptly when the flushing device is switched on, but rather increases in a damped manner. This can prevent pressure drops on the low pressure side.
  • the viscosity-dependent throttle can be formed by a hole or a gap.
  • an annular gap can be used.
  • the length of the bore or the gap is advantageously more than twice as large as the diameter of the bore or the height of the gap. Further advantageously, the length of the bore or the gap is more than three times, furthermore advantageously more than five times the diameter of the bore or the height of the gap. In this way, a corresponding dependence of the flow rate through the throttle on the viscosity of the hydraulic fluid can be achieved.
  • the throttle is particularly advantageously designed as a cylindrical annular gap.
  • the inside diameter of the cylinder can be between 0.5 times and 2 times the gap length, further advantageously between 0.8 times and 1.2 times the gap length.
  • the exit fluid flow can flow directly through the viscosity-dependent throttle, and can thus be controlled directly through the throttle depending on its viscosity.
  • the flushing device comprises a two-stage valve with a main piston for controlling the outlet fluid flow and a control stage, the viscosity-dependent throttle being arranged in the control stage.
  • the increasing amount of throttle due to the decreasing viscosity thus ensures a higher control current, through which the main piston is likewise deflected accordingly in order to generate an increased feed fluid flow.
  • a throttle piston is provided for setting a defined pressure difference via the viscosity-dependent throttle, which is acted upon by the inlet pressure of the flushing device.
  • the throttle piston is advantageously arranged behind the viscosity-dependent throttle and controls the flow of the hydraulic fluid to the tank.
  • the throttle piston can form a pressure control valve which is acted upon on one side with the pressure on the inlet side of the flushing device and on the other side with the pressure behind the viscosity-dependent throttle.
  • a throttle piston can be provided if the viscosity-dependent throttle is arranged in the control stage of a two-stage valve.
  • a change-over valve is also provided in the present invention, through which the outlet fluid flow is always taken from the side of the hydraulic circuit on which the lower load pressure is present.
  • This lower load pressure usually corresponds to the feed pressure.
  • the shuttle valve and the viscosity-dependent throttle can be designed separately.
  • a shuttle valve can be used the viscosity-dependent throttle or a two-stage valve, in the control stage of which the viscosity-dependent throttle is arranged, are connected in series.
  • the viscosity-dependent throttle can be integrated in the switching valve.
  • the switching valve advantageously has a piston and is designed such that the piston is acted upon on opposite sides by the pressure of the two sides of the closed hydraulic circuit. Depending on the pressure conditions, the piston releases the connection between one or the other side with the tank, the piston connecting the low-pressure side to the tank.
  • connection between the low-pressure side and the tank takes place in each case via a viscosity-dependent throttle, which according to the invention thus adjusts the feed fluid flow as a function of the temperature of the hydraulic fluid.
  • a viscosity-dependent throttle which according to the invention thus adjusts the feed fluid flow as a function of the temperature of the hydraulic fluid.
  • two viscosity-dependent throttles are provided, each associated with one side of the closed hydraulic circuit.
  • At least one pilot piston can be provided in the piston, which prevents a flushing flow below a certain minimum pressure on the low pressure side.
  • the pilot piston can be biased against a spring force which must first be overcome by the pressure on the low pressure side in order to enable a flushing flow.
  • the length of the viscosity-dependent throttle is set by the pressure difference between the high and the low pressure side.
  • the length of the throttle advantageously decreases with an increase in the pressure difference, so that a correspondingly higher volume flow is achieved with a higher pressure difference.
  • the viscosity-dependent throttle is advantageously formed by an annular gap between the piston and a valve housing, the length of the viscosity-dependent throttle changing when the piston is displaced.
  • the flushing device has a temperature sensor, via which a control valve for controlling the outlet fluid flow is activated.
  • a control valve for controlling the outlet fluid flow is activated.
  • This enables an even more flexible control of the exit fluid flow based on the temperature.
  • the exit fluid flow can be increased with increasing temperature and reduced with decreasing temperature.
  • the temperature of the hydraulic fluid is advantageously regulated to a predetermined temperature by the flushing device. In particular, this temperature can be adjustable.
  • An electronic control is advantageously used for evaluating the data of the temperature sensor and for controlling the control valve.
  • At least one pressure sensor can also be provided, the outlet fluid flow being controlled on the basis of the data from the pressure sensor.
  • the outlet fluid flow is advantageously controlled as a function of the pressure difference between the high and low pressure sides.
  • the outlet fluid flow can be increased as the pressure difference increases.
  • the exit fluid flow can be controlled as a function of the pressure on the low pressure side.
  • the exit function only starts at a certain minimum pressure on the low pressure side. This can prevent the occurrence of sudden pressure drops due to the insertion of the outlet.
  • a pressure reducing valve in combination with an orifice or a proportional flow control valve can be provided as the control valve.
  • the control valve for controlling the outlet fluid flow can be designed separately from a switching valve or combined with it.
  • a 2-way proportional flow control valve can be provided, which also serves as a switching and control valve.
  • the present invention is particularly preferably used in a hydraulic system whose feed pump is designed as a variable displacement pump.
  • the power loss through the feed pump can be reduced, the feed quantity consumed and thus the power loss being reduced as a result of the need-based feed-out of the hydraulic fluid according to the present invention.
  • the feed pump is advantageously controlled as required.
  • the feed pump can be designed as a pressure regulator.
  • a flushing device for a hydraulic system as described above is also presented as an illustrative example.
  • the flushing device comprises a viscosity-dependent throttle. Furthermore, the flushing device is advantageously constructed as described above.
  • the flushing device according to the invention can have a temperature sensor and a control valve which is controlled as a function of the temperature measured by the temperature sensor.
  • the flushing device can include a shuttle valve.
  • the shuttle valve can form a separate element or can be combined with one of the other components of the flushing device, in particular the viscosity-dependent throttle or the control valve.
  • Advantageous configurations have also already been described above.
  • a method for operating a hydraulic system is shown with a closed hydraulic circuit comprising a hydraulic pump and a hydraulic motor with a flushing device for discharging a part of the hydraulic fluid from the closed circuit.
  • the method according to the invention is characterized in that the exit fluid flow is changed as a function of the temperature of the hydraulic fluid.
  • the outlet fluid flow is increased as the temperature increases and / or the outlet fluid flow is reduced as the temperature decreases.
  • the method advantageously serves to operate a hydraulic system as described above. Further advantageously, the hydraulic system is operated in the manner that has also already been described above.
  • the present invention enables flushing according to need by taking the circuit temperature into account. This improves the energetic design of the flushing function. Furthermore, a sudden switching on of the flushing is prevented, which would otherwise lead to a drop in feed pressure, as in the prior art.
  • the present invention is particularly advantageously combined with a variable feed, so that a corresponding energy saving can be achieved.
  • FIG. 1 a closed hydraulic circuit according to the present invention is shown schematically.
  • a hydraulic pump 1 is provided, which conveys hydraulic fluid and drives the hydraulic motor 2. The amount of oil it exits is returned directly to pump 1.
  • volumetric losses in the closed hydraulic circuit are compensated for by means of a feed pump 5, which is connected to the two load sides A and B of the closed hydraulic circuit via check valves 6.
  • the present closed hydraulic circuit is a hydraulic circuit with two flow directions, so that depending on the pumping direction of the pump 1, either the load side A or the load side B works as a high pressure side, while the other side works as a low pressure side.
  • the pump 1 and / or the motor 2 can be designed as an adjustment unit. Furthermore, the pump 1 can be driven by a motor 4, while the hydraulic motor 2 drives a device 3.
  • the lower load pressure (generally corresponds to the feed pressure) of a flushing device 8 according to the invention is now supplied via the shuttle valve 7 in order to feed out part of the hot oil from the circuit and thus to avoid overheating.
  • the flushing device 8 according to the invention is in here Figure 1 drawn as a separate unit to the shuttle valve 7, but can also be combined with this.
  • the shuttle valve 7 is designed in such a way that, from a certain pressure difference between the load side A and the load side B, a flushing function begins and a certain flow of exit fluid is discharged.
  • the rinsing device 8 is now designed such that this feed fluid flow depends on the temperature of the hydraulic fluid. In this way, a flush that is tailored to the needs is achieved.
  • the present invention makes use of the fact that the viscosity of the hydraulic fluid drops with increasing temperature.
  • the exit fluid flow can therefore be variable as a function of the temperature by means of a viscosity-dependent throttle, so that a lot of exit fluid flow is produced when the oil is hot, and the temperature in the closed circuit can thus be reduced.
  • the length of the gap is more than twice as large as its height, advantageously more than five times and furthermore advantageously more than ten times. If a bore is used, its length is advantageously also more than twice as large as its diameter, furthermore advantageously more than five times and furthermore advantageously more than ten times.
  • such a viscosity-dependent throttle point can be arranged behind the shuttle valve 7 as a flushing device 8.
  • the throttling point only has to be dimensioned so that sufficient exit fluid flow is generated.
  • FIG Figure 2a An embodiment of a flushing device according to the invention, in which a two-stage flushing valve 20 is used instead, is shown in FIG Figure 2a shown.
  • This comprises a main piston 21 with a central throttle point 22.
  • the main piston 21 determines the exit fluid flow by opening or closing the connection between the inlet side of the valve and the main opening 25, which leads to the tank, depending on its position.
  • the piston 21 is biased by a spring 24 against the pressure on the input side.
  • the fluid is led through the throttle point 22 in the main piston 21 to the viscosity-dependent measuring point 23, which according to the invention is designed as a viscosity-dependent throttle.
  • the measuring point 23 can be designed as a long cylindrical annular gap, as shown in the exemplary embodiment.
  • the geometric relationships are ideally such that the diameter of the cylindrical annular gap is in the range of the gap length.
  • a long calibration bore could also be used, the length of the calibration bore advantageously corresponding to at least five times the diameter of the bore.
  • the lower load pressure in the closed circuit is always supplied to the flushing valve 20 via the shuttle valve 7.
  • FIG. 2b Another embodiment is now shown with a two-stage valve, in which the main stage and the measuring point as in the in Figure 2a shown variant is executed.
  • pressure compensation is also provided.
  • a throttle piston 29 is provided, which controls the volume flow from the measuring point 23 to the relief bore 28.
  • the inlet pressure Px at the purge valve 20 is guided to the rear of the throttle piston 29, which is biased against this pressure by a spring 27.
  • the throttle piston 29 in combination with the spring 27 thus throttles the control current with respect to the relief bore 28.
  • the pressure difference across the measuring point 23 can be kept constant regardless of the level of the inlet pressure Px.
  • the advantage is that no variation in the exit fluid flow is caused by feed pressure variations.
  • An annular gap acting according to the invention as a viscosity-dependent throttle can, as in Figures 2a and 2 B shown, are made available by a cylinder, which is inserted into a correspondingly larger hollow cylinder, for example screwed.
  • the throttle piston 29 is arranged in a bore within this cylinder, where the Control current from the measuring point 23 is guided through a bore 26 through the cylinder wall into the bore inside the cylinder.
  • FIG 3 An embodiment of such a shuttle valve is shown.
  • a piston 31 is provided, which is deflected against the springs 32 due to the pressure difference between the sides A and B.
  • the low-pressure side is in each case connected to the tank connection T via an annular gap 33 which acts as a viscosity-dependent throttle, so that a temperature-dependent feed fluid flow is established.
  • This example has the further advantage that with increasing pressure difference in the closed circuit, the piston 31 deflects more and more against the springs 32. As a result, the effective annular gap 33 becomes shorter and the feed fluid flow increases in inverse proportion to the length of the annular gap 33. Furthermore, damping of the movement of the piston 31 can be provided. For example, the increase in the feed fluid flow can be delayed over the bore 34 in the event of a sudden increase in load pressure. In this way, feed pressure drops in the closed circuit can be prevented. Basically, however, more feed fluid flow is generated at high load pressures. Furthermore, the tank line T can be used as a limitation of the maximum feed fluid flow, e.g. B. by combination with a limiting nozzle.
  • a piston 47 is provided, which deflects against the springs 46 due to a pressure difference between A and B and thereby connects the respective low-pressure side to the tank connection T via the corresponding annular gap 44.
  • the piston 47 is now designed as a bushing, in which pilot pistons 41 and 41 'are provided for the sides B and A, respectively.
  • the respective connection point 43 is opened so that hydraulic fluid can flow from the measuring point 44 via the connection point 43 through the interior of the pilot piston 49 and the interior of the bushing 47 to the tank connection T.
  • the bushing 47 can be damped to achieve a time delay, similar to the bore 34 in Fig. 3 .
  • the feed fluid flow is adjusted as a function of viscosity.
  • a viscosity-dependent output fluid flow generation can optionally be combined with the functions already described, such as an alternating function, a switching function, a load pressure dependency, damping and a setting of a maximum output fluid flow.
  • the feed-out can also be implemented via a temperature measurement and a correspondingly controlled control valve.
  • a control loop with temperature measurement can be provided.
  • FIG. 5 a corresponding embodiment of a hydraulic circuit is shown.
  • the circuit temperature is measured at a suitable point in the closed circuit by means of a temperature sensor 51.
  • this measurement could optionally also take place after the shuttle valve 7.
  • an actuator 54 is now controlled, which draws a controllable feed fluid flow from the circuit.
  • a changeover valve 43 can be connected upstream of this actuator, or the actuator 54 can already be equipped with the changeover function.
  • valve types / systems are conceivable as actuators:
  • a pressure reducing or reducing valve can be used, which allows fluid to flow through a diaphragm at variable pressure.
  • Such a valve is then advantageously combined with a shuttle valve.
  • a 2-way proportional flow control valve can be used, which also serves as a shuttle valve and via which the exit fluid flow can be adjusted.
  • the electronic control also enables other monitoring and control functions to be integrated.
  • at least one pressure sensor can be provided for the pressure in the hydraulic circuit, advantageously one pressure sensor each for side A and side B.
  • the electronic control 52 monitors the feed pressure level in order to switch off the flushing when the feed pressure level drops. As a result, the entire amount of food is available for filling the circuit.
  • the flushing devices of the present invention are advantageously used in a hydraulic system with a feed pump 5 designed as a variable displacement pump.
  • a feed pump 5 designed as a variable displacement pump.
  • such a feed pump can work as required and be designed, for example, as a pressure regulator. In this way, a needs-based and thus energy-saving feed is realized.

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

Claims (11)

  1. Système hydraulique avec un circuit hydraulique fermé composé d'une pompe hydraulique (1) et d'un moteur hydraulique (2), avec une pompe d'alimentation (5) servant à compenser des pertes de volume dans le circuit fermé et avec un dispositif de rinçage (8) servant à évacuer une partie du liquide hydraulique hors du circuit fermé, dans lequel le dispositif de rinçage (8) présente un étranglement (33, 44) dépendant de la viscosité de sorte que l'écoulement de fluide d'évacuation dépend de la température du fluide hydraulique,
    caractérisé en ce que
    la longueur de l'étranglement (23, 33, 44) dépendant de la viscosité peut être réglée par la différence de pression entre le côté haute pression et le côté basse pression.
  2. Système hydraulique selon la revendication 1, dans lequel l'étranglement (23, 33, 44) dépendant de la viscosité est formé par un alésage ou une fente, en particulier une fente annulaire, dans lequel de manière avantageuse la longueur de l'alésage ou de la fente est plus de deux fois plus grande que le diamètre de l'alésage ou la hauteur de la fente, de manière avantageuse est plus de trois et par ailleurs de manière avantageuse plus de cinq fois plus grande.
  3. Système hydraulique selon la revendication 1 ou 2, dans lequel le dispositif de rinçage comprend une soupape (20) à deux étages avec un piston principal (21) servant à piloter l'écoulement de fluide d'évacuation et un étage de commande, dans lequel l'étranglement (23) dépendant de la viscosité est disposé dans l'étage de commande.
  4. Système hydraulique selon l'une quelconque des revendications 1 à 3, dans lequel pour régler une différence de pression définie par l'intermédiaire de l'étranglement (23) dépendant de la viscosité, un piston d'étranglement (29) est prévu, lequel est soumis à l'action de la pression d'entrée du dispositif de rinçage, dans lequel le piston d'étranglement (29) est disposé de manière avantageuse derrière l'étranglement (23) dépendant de la viscosité et commande le flux du fluide hydraulique vers le réservoir.
  5. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel l'étranglement (33, 44) dépendant de la viscosité est intégré dans une soupape de commutation, laquelle relie respectivement le côté basse pression du circuit hydraulique fermé au réservoir.
  6. Système hydraulique selon la revendication 5, dans lequel la soupape de commutation présente un piston (31, 47) et est réalisée de telle sorte que le piston est soumis sur des côtés se faisant face à l'action de la pression des deux côtés (A, B) du circuit hydraulique fermé, dans lequel le piston (31, 47) relie de manière avantageuse respectivement le côté basse pression par l'intermédiaire d'un étranglement (33, 44) dépendant de la viscosité au réservoir, dans lequel de manière avantageuse deux étranglements (33, 44) dépendant de la viscosité associés respectivement à un côté du circuit hydraulique fermé sont prévus.
  7. Système hydraulique selon la revendication 5 ou 6, dans lequel au moins un piston pilote (41) est prévu dans le piston (47), lequel empêche un écoulement de fluide d'évacuation sous une certaine pression minimale sur le côté basse pression.
  8. Système hydraulique selon la revendication 6 ou 7, dans lequel l'étranglement ou les étranglements dépendants de la viscosité est formé ou sont formés par une fente annulaire entre le piston (31, 47) et un carter de soupape, dans lequel la longueur de l'étranglement dépendant de la viscosité se modifie lors d'un coulissement du piston.
  9. Système hydraulique avec
    un circuit hydraulique fermé composé d'une pompe hydraulique (1) et d'un moteur hydraulique (2),
    une pompe d'alimentation (5) servant à compenser des pertes de volume dans le circuit fermé, et
    un dispositif de rinçage (8) servant à évacuer une partie du fluide hydraulique hors du circuit fermé, dans lequel
    le dispositif de rinçage (8) est réalisé de telle sorte que l'écoulement de fluide d'évacuation dépend de la température du fluide hydraulique,
    le dispositif de rinçage présente un capteur de température (51), une soupape de commande (54) servant à piloter l'écoulement de fluide d'évacuation et une commande (52) électronique servant à évaluer les données du capteur de température (51) et servant à piloter la soupape de commande (54), et
    le dispositif de rinçage régule la température du fluide hydraulique sur une température prédéfinie,
    caractérisé en ce que
    un capteur de pression est prévu, dans lequel l'écoulement de fluide d'évacuation est piloté en fonction de la différence de pression entre le côté haute pression et le côté basse pression et/ou en fonction de la pression sur le côté basse pression.
  10. Système hydraulique selon la revendication 9, dans lequel une soupape de réduction de pression est prévue en combinaison avec un diaphragme ou une soupape de régulation de débit proportionnelle en tant que soupape de commande (54), dans lequel de manière avantageuse une soupape de régulation de débit proportionnelle à deux voies est prévue, laquelle fait office simultanément de soupape de commutation.
  11. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel la pompe d'alimentation (5) est réalisée en tant que pompe d'ajustement et est pilotée par ailleurs de manière avantageuse selon les besoins.
EP12005536.3A 2012-01-04 2012-07-30 Hydraulic system Active EP2613058B1 (fr)

Applications Claiming Priority (1)

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CH00010/12A CH705960A1 (de) 2012-01-04 2012-01-04 Hydrauliksystem mit temperaturabhängiger Hydraulikfluidleckage.

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EP2613058A3 EP2613058A3 (fr) 2017-05-10
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EP2918876B1 (fr) 2014-03-05 2018-02-28 BOMAG GmbH Procédé de fonctionnement d'un système hydraulique d'une finisseuse de route automotrice, système hydraulique, en particulier destiné à exécuter le procédé et finisseuse de route dotée d'un tel système hydraulique
DE102015213936A1 (de) * 2015-07-23 2017-01-26 Danfoss Power Solutions Gmbh & Co. Ohg Spüleinrichtung für hydrostatische Vorrichtung
DE102017215726A1 (de) * 2017-09-07 2019-03-07 Robert Bosch Gmbh Hydrostatische Ventilanordnung, hydrostatisches Getriebe mit der Ventilanordnung, und hydrostatischer Antrieb mit dem Getriebe
DE102018208352A1 (de) 2018-05-28 2019-11-28 Robert Bosch Gmbh Hydraulische Spülventilanordnung
JP7153539B2 (ja) * 2018-11-26 2022-10-14 Ｋｙｂ株式会社 流体圧駆動装置
CN113565834B (zh) * 2021-07-02 2024-07-12 中冶宝钢技术服务有限公司 一种静液压行走驱动循环冲洗控制系统
CN116146705B (zh) * 2022-12-28 2023-10-27 山东临工工程机械有限公司 具有散热功能的液压系统及工程机械车辆

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US20100095665A1 (en) * 2008-10-21 2010-04-22 Caterpillar Inc. Hydrostatic pump and motor with improved torque reversal characteristics

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EP2613058A3 (fr) 2017-05-10
EP2613058A2 (fr) 2013-07-10

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