EP2985469B1 - Entrainement hydrostatique et dispositif de soupape associe - Google Patents

Entrainement hydrostatique et dispositif de soupape associe Download PDF

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Publication number
EP2985469B1
EP2985469B1 EP15177835.4A EP15177835A EP2985469B1 EP 2985469 B1 EP2985469 B1 EP 2985469B1 EP 15177835 A EP15177835 A EP 15177835A EP 2985469 B1 EP2985469 B1 EP 2985469B1
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EP
European Patent Office
Prior art keywords
pressure
piston chamber
section
opening cross
pressure medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15177835.4A
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German (de)
English (en)
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EP2985469A1 (fr
Inventor
Edwin Heemskerk
Werner Herfs
Michael Brand
Mircea Chima
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • 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
    • F15B2011/0243—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 the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy

Definitions

  • the invention relates to a hydraulic drive according to the preamble of patent claim 1.
  • a hydraulic cylinder for moving loads, in particular for lifting and lowering, a hydraulic cylinder, in particular a double-acting, is used.
  • This has two piston chambers, which are separated by a piston.
  • An external load acts on a piston rod connected to the piston.
  • there is a need to be able to recover energy This can be done, for example, when potential energy of an elevated load when lowering the load is free again.
  • the document shows DE 10 2012 003 320 A1 a hydrostatic drive in which hydraulic fluid flowing from the hydraulic cylinder can be passed via a valve device to a hydraulic motor and / or a hydraulic accumulator.
  • a fan of an internal combustion engine can be driven.
  • Pressure medium for driving this hydraulic motor or a hydraulic motor assisting the internal combustion engine can be taken from the hydraulic accumulator.
  • Solutions are also known in which an electric generator or a flywheel can be driven via the outflowing pressure medium or the hydraulic accumulator receiving the pressure medium.
  • a disadvantage of this concept is that the hydraulic component receiving the outflowing pressure medium-that is to say the hydraulic motor or the hydraulic accumulator-must be designed for the maximum pressure medium volume flow occurring at the maximum speed of movement of the hydraulic cylinder.
  • maximum movement speed comparatively rarely occurs, at most about half of the operating time, so hydraulic components large capacity must be kept, the bulk operating time far below their capacity, which adversely affects the cost and efficiency of the drive.
  • the publication DE 10 2008 034 301 A1 shows in this regard a solution with a regeneration of the effluent from the decreasing piston chamber pressure medium.
  • a direct pressure medium connection of the two piston chambers is proposed, so that a portion of the outflowing pressure medium, bypassing the hydraulic pump, can flow into the other piston chamber. Due to this regeneration, the hydraulic pump can be made smaller, which reduces the cost of the drive and in particular allows the operation of the hydraulic pump with higher efficiency, since the hydraulic pump can work because of their smaller size over a longer period of operation in the range of their maximum delivery volume.
  • the invention is therefore the object of the invention to provide a generic hydrostatic drive, which is better protected against cavitation, which are reduced as a result, the cost.
  • the invention is therefore the object of the invention to provide a generic hydrostatic drive, which is better protected against cavitation, which are reduced as a result, the cost.
  • a hydrostatic drive has a particularly double-acting hydraulic cylinder for moving, in particular for lifting and / or lowering, a load, and for recuperation (recovery) of hydraulic power of the hydraulic cylinder a hydraulic machine and / or a hydraulic accumulator.
  • potential and / or kinetic energy of the load can be recovered via the hydraulic machine or the storage.
  • two piston chambers are fluidly separated from each other by a piston, of which a piston chamber is fluidically connectable to the hydraulic machine and / or the reservoir via a first pressure medium connection.
  • the drive has a second pressure medium connection via which the other piston chamber can be supplied with a partial volume flow of a discharge volume flow flowing away from a piston chamber.
  • a third pressure medium connection connected in parallel with the second pressure medium connection is provided. Also via these, the other piston chamber can be supplied with a partial volume flow of the outflow volume flow of the one piston chamber.
  • the third pressure medium connection has a third throttle device with an invention according to the pressure of the other piston chamber adjustable, third opening cross-section. The third pressure medium connection can thus be controlled via the third throttle device.
  • the movement of the load for a direction of movement of the piston forcibly leads to a reduction of the one piston chamber and to an enlargement of the other piston chamber.
  • the pressure medium flowing out of the one piston chamber is proportionally conducted via the second pressure medium connection into the enlarging other piston chamber, which can be referred to as regeneration of pressure medium.
  • a pressure medium source in particular a hydraulic pump or a hydraulic accumulator, which is to be provided for providing the pressure medium volume flow for the other piston chamber, therefore no longer has to be designed for the maximum pressure medium volume flow of the other piston chamber due to the maximum movement speed. It can instead be designed smaller, so that investment and operating costs can be saved and the cost of the drive can be reduced.
  • the previously discussed cavitation in the other piston chamber can be prevented according to the invention well over the third throttle device with the adjustable depending on the pressure of the other piston chamber third opening cross-section.
  • the third opening cross-section can preferably be controlled as a function of the increasing pressure of the other piston chamber, it being possible for the third opening cross-section to be openable as a function of the decreasing pressure of the other piston chamber.
  • the third throttle device has in a preferred development, in particular an adjustable pressure equivalent, with which the third throttle device, in particular a throttle body or valve body, is loaded in the direction of a control of the third opening cross-section. In this way, cavitation is prevented in the other piston chamber and the pressure in the other piston chamber is less than or equal to the set third pressure equivalent, so that a pressure gain is limited.
  • the second pressure medium connection proves to be particularly advantageous when the hydraulic cylinder is designed such that the partial volume flow can completely cover the pressure medium volume flow necessary for filling the other piston space. Then, this pressure medium volume flow is completely regenerated from the drain volume flow and it may even be considered to dispense entirely with a hydraulic pump.
  • the hydraulic machine is formed via a hydraulic motor for converting hydraulic energy of the drain volume flow into mechanical energy.
  • the mechanical energy can be used, for example, to drive other hydraulic machines, a generator, a flywheel or supporting the drive of an internal combustion engine.
  • the stored pressure medium energy can be used offset in time if necessary.
  • the hydraulic machine can be designed with a constant or variable displacement volume.
  • the hydraulic machine can be designed as an axial piston machine in swash plates or Schrägachsenbauweise.
  • the swashplate design with adjustable displacement volume running hydraulic machine can be designed with swivel swash plate be, whereby a change between engine and pump operation, or vice versa, is made possible by a simple swinging.
  • a drive shaft of the hydraulic machine may be connected to a drive shaft of a diesel engine or an electric motor and / or generator or to a mechanical flywheel.
  • the first pressure medium connection of the drive in a preferred development has a first throttle device with an adjustable, first opening cross section.
  • the first throttle device is preferably designed in such a way that it allows a substantially leak-free load hold in the non-actuated state of the hydraulic cylinder.
  • the first throttle device is preferably designed as a continuously adjustable 2/2-way seat valve that is biased in a blocking position of its valve seat, in particular by a spring and actuated in the direction of flow positions.
  • the actuation can be designed hydraulically, mechanically or electromagnetically.
  • the first throttle device is attached directly to the hydraulic cylinder, in particular flanged, so that it can fulfill the function of a pipe rupture protection.
  • the piston then has a piston surface, of which the piston space is at least partially limited. Preferably, this is larger than another piston surface of the piston, of which the other piston chamber is at least partially limited. The regeneration from the piston chamber with the larger piston surface to the piston chamber with the smaller piston surface thus takes place via the second pressure medium connection.
  • the hydraulic cylinder is designed such that the piston is connected to a piston rod, from which the other piston chamber is penetrated and at which the load acts.
  • the second pressure medium connection of the drive in a preferred development has a second throttle device with a second opening cross section which is adjustable as a function of the pressure of the piston space.
  • the second throttle device is designed such that its pressure drop, more precisely its flow resistance, via the second opening cross-section, at least when it is largely turned on, is low.
  • the first opening cross-section of the first throttle device This can be achieved in a piston chamber via the second pressure medium connection, the pressure gain. In a piston chamber then prevails due to the second pressure medium connection, a higher pressure than without the second pressure medium connection.
  • the second opening cross section can be controlled as a function of the increasing pressure of the one piston chamber, wherein it can be opened in dependence on the decreasing pressure of the one piston chamber.
  • the second opening portion is controllable in this way in a predetermined interval of the pressure of a piston chamber. In this way, depending on the pressure of a piston chamber and depending on its tendency (rise, sink), the partial volume flow can be reduced or increased. The more the second opening cross-section is opened, the stronger the effect previously discussed pressure boost.
  • the second pressure medium connection according to the invention is completely interrupted and the pressure gain comes to a standstill. In this way it is ensured that a predetermined maximum load can be held by the hydraulic cylinder.
  • the control of the second opening cross-section by the second throttle device - in particular a throttle or valve body of the second throttle device - is loaded in the direction of a Zu Kunststoffung the second opening cross section with the pressure of a piston chamber.
  • a lower or minimum pressure equivalent with which it - in particular its throttle or valve body - is loaded in the direction of a control of the second opening cross-section.
  • a limit value of the pressure of the one piston chamber can thus be preset, from which the second pressure medium connection is controlled. From this closing point, or from reaching this limit, the second opening cross-section is reduced with increasing pressure, whereby the partial volume flow is throttled.
  • the second throttle device is designed such that the second opening cross-section is substantially constant controlled as long as the pressure of a piston chamber is smaller than the lower pressure equivalent. Consequently, in this pressure range, the pressure of one piston chamber has no influence on the partial volume flow, and the advantages of pressure amplification and reduction of the pressure medium volume flow to be supplied by the hydraulic pump are fully realized.
  • the second opening cross section can be controlled substantially in proportion to the increasing pressure of the one piston chamber, as long as the pressure of the one piston chamber rises above the lower pressure equivalent.
  • the pressure gain in this pressure range is increasingly reduced.
  • the second throttle device has an upper pressure equivalent, with which it is loaded in the direction of a control of the second opening cross-section and which is greater than the first pressure equivalent.
  • the upper pressure equivalent By way of the upper pressure equivalent, a closing pressure is thus established for the pressure of the one piston chamber, from which the second opening cross section has been closed and the partial volume flow has become approximately zero and the pressure boost is thereby switched off.
  • the drive according to the invention the third pressure medium connection and / or the previously discussed hydraulic pump is provided which can provide this Nachsaugvolumenstrom required and thereby prevents cavitation in the other piston chamber.
  • the drive can be developed such that the second throttle device has a Restö Stammsquer bain as soon as the pressure of a piston chamber is approximately equal to the upper pressure equivalent or greater than this. By means of the residual opening cross section, sufficient pressure medium can then always be fed into the other, enlarging piston space.
  • the residual opening cross-section is designed such that in the other piston chamber a pressure is established which is limited and prevented by cavitation.
  • the lower and / or the upper pressure equivalent is formed via at least one compression spring.
  • both mentioned pressure equivalents are formed by a common spring.
  • other technical solutions such as electromagnetic or hydraulic, for applying the pressure equivalents or possible.
  • the lower pressure equivalent and / or the upper pressure equivalent is configured adjustable.
  • the spring force is preferably adjustable.
  • the hydraulic pump is part of the hydrostatic drive.
  • the hydraulic pump is part of the hydrostatic drive.
  • the drive is preferably used in a mobile work machine, since there due to always tight space and the requirement of a low vehicle weight fiction reduction of the hydromachine (due to the described pressure boost) and the hydraulic pump (due to the regeneration described) prove to be particularly advantageous.
  • valve device of the hydrostatic drive which is designed according to at least one of the aspects of the preceding description, is embodied in a further development in a compact block or disk construction.
  • the valve device has the second throttle device with the second opening cross section, which is adjustable as a function of the pressure of the one piston chamber, via which the second pressure medium connection can be controlled.
  • it has the second pressure medium connection connected in parallel, third pressure medium connection, via which the other piston chamber with the partial volume flow of the drain volume flow can be supplied.
  • the third throttle device is provided with the third opening cross-section which is adjustable as a function of the pressure of the other piston chamber and via which the third pressure medium connection can be controlled.
  • a hydrostatic drive 1 has a hydraulic cylinder 2 for moving, in particular for lifting and / or lowering a load, which is symbolized by the designation F L.
  • the hydraulic cylinder raises and lowers the load F L under the action of gravity in FIG. 1 in the direction of the arrow marked x acts.
  • the hydraulic cylinder 2 has a piston 4 which is received axially displaceably in a housing 6 of the hydraulic cylinder 2. From the piston 4, a cylinder bottom side piston chamber 8 is fluidically separated from a piston rod side, other piston chamber 10 in the housing 6.
  • the piston 4 has on the cylinder bottom side a piston surface 12, of which the one piston chamber 8 is limited in sections, and on the other hand another piston surface 14, of which the other piston chamber 10 is partially limited.
  • a piston rod 16 is attached to the piston 4, to which the load F L attacks.
  • first pressure medium connection 18 By way of a first pressure medium connection 18, one piston chamber 8 is connected to a working connection of a hydraulic machine 20 designed as a hydraulic motor with an adjustable displacement.
  • the first pressure medium connection 18 has a first throttle device 22 with an adjustable, first opening cross-section, via which the first pressure medium connection 18 can be opened and closed.
  • the other piston chamber 10 is connected to a working port of a hydraulic displacement pump 24 configured with an adjustable displacement volume.
  • the hydrostatic drive 1 additionally has a second pressure medium connection 26 branching off from the first pressure medium connection, via which the one piston space 8 can be fluidically connected to the other piston space 10 for a so-called regeneration operation.
  • Regenrations vulgar takes place the Pressure medium supply of the other piston chamber 10 partially or completely via the second pressure medium connection 26, that is, a partial flow of the effluent from a piston chamber 8 drain volume flow.
  • the second pressure medium connection 26 is designed as a simple adjusting throttle second throttle device 28 is arranged.
  • the second throttle device 28 is formed in the first embodiment as a simple adjusting throttle. About them, the second pressure medium connection 26 and thus the partial volume flow can be controlled.
  • FIG. 2 shows a second example of a hydrostatic drive 101, which substantially according to FIG. 1 is the same, and as a sole difference instead of the hydraulic motor has a hydraulic accumulator 121. Through this, the pressure medium energy of the whole or of the partial volume flow reduced drain volume flow can be stored for later use.
  • a third example of a hydrostatic drive 201 according to FIG. 3 corresponds largely to that according to FIG. 1 ,
  • a second throttle device 228 is arranged in the second pressure medium connection 26, which has a second opening cross section A 2 which is adjustable as a function of the pressure p A and via which the second pressure medium connection 26 can be actuated and controlled.
  • the second throttle device 228 is configured in the example as a proportionally adjustable 2/2-way valve.
  • a valve body of the second throttle device 228 is loaded in the direction of a blocking position 228b with the pressure p A , whereas it is loaded in the direction of an open position 228a with a pressure equivalent, namely the spring force of a spring 230.
  • the spring 230 acts with a spring force on the valve body, which corresponds to a lower pressure equivalent p Au .
  • the spring 230 acts with a spring force which corresponds to an upper pressure equivalent p Ao .
  • the third example according to FIG. 3 takes advantage of the two examples described above (regeneration solution) and combines this with a higher utilization of the recuperable from the piston chamber 8 pressure medium energy. It is the second throttle device 228 designed such that its pressure loss is low. In particular, when the first throttling device 22 is fully opened, the pressure p B in the other piston chamber 10 is then approximately equal to the pressure p A in a piston chamber 8. It follows that the pressure p A increases further. This results in the following a new balance of forces on the piston 4 with an increased compared to the aforementioned examples pressure p A.
  • the drain volume flow towards the hydraulic motor 20 can be approximately halved with this approach, and the pressure p A and thus the working pressure of the hydraulic motor 20 can be approximately doubled.
  • the hydraulic pressure medium energy supplied to the hydraulic motor 20 via the outflow volume flow is approximately the same as in the preceding examples, the hydraulic motor 20 can be designed to be half as large. As a result, the drive 201 is particularly cost-effective.
  • the second pressure medium connection 26 is controlled as a function of the pressure p A in a piston chamber 8 when it rises above a certain threshold value.
  • the above-described load of the valve body of the second throttle device 228 serves in the direction of the blocking position 228b with the tapped by a piston chamber 8 pressure p A.
  • the tap is carried out via a load signaling line 232, between the one piston chamber 8 and the first throttle device 22 of the first Pressure medium connection 18 branches off.
  • the closing of the second pressure medium connection 26, or of the second opening cross-section A 2 begins according to the diagram in FIG FIG.
  • the values for the pressure equivalents p Au , p Ao which determine the control behavior of the second throttle device 28, depend on the maximum permissible pressure p Amax in a piston chamber 8. In addition, an operating strategy plays a role.
  • p Ao could also be designed for the value of the maximum pressure p Amax . Even then, the pressure p A in a piston chamber 8 can not statically exceed the value p Amax , since the pressure p A is tapped via the load reporting line 232 directly in a piston chamber 8 and reported to the second throttle device 228. However, this type of design for p Ao in dynamic load cases proves to be critical.
  • the lower pressure equivalent p Au is designed so that the second throttle device 228 has a stable control behavior. In the exemplary embodiment shown, this is given when p Au is about 50 bar lower than p Ao (140 bar).
  • FIG. 3 A weakness of in FIG. 3 As shown, it is that at operating times, where the load F L is so large that the second throttle device 228 is controlled (blocking position 228 b), the inlet flow into the other piston chamber 10 must be supplied from another location.
  • the reserved hydraulic pump 24 could serve this purpose.
  • the pressure medium volume flow of the hydraulic pump 24 is a limiting factor in parallel operation of a plurality of hydraulic consumers. If, at their maximum utilization, the additional suction volume flow required by the other piston chamber 10 is added and the second pressure medium connection 26 is closed as mentioned, cavitation may occur in the other piston chamber 10 due to the lack of pressure medium supply and / or the other hydraulic consumers due to insufficient supply through the hydraulic pump 24 slower.
  • the drive 201 according to the invention is according to an in FIG. 4 shown embodiment of a hydrostatic drive 301 is supplemented by a third pressure medium connection 340 which is connected in parallel to the second pressure medium connection 26 and branches off from the first pressure medium connection between the first throttle device 22 and the working port of the hydraulic motor 20.
  • a third throttle device 342 is provided, the third opening cross section of which can be controlled as a function of the pressure p B of the other piston chamber 10. More specifically, one is Valve body of the third throttle device 342 in the direction of an open position of the third throttle device 342 with the pressure equivalent of a spring 344 and loaded in the direction of a closed position with the pressure p B of the other piston chamber 10. With decreasing pressure p B of the third opening cross section is thus controlled by the spring 344, whereby the above-described cavitation is prevented by undersupply of the other piston chamber 10.
  • the third throttle device 342 may also be referred to as a suction valve.
  • the spring force / pressure equivalent of the spring 344 is adjustable and adjusted to about 10 bar.
  • FIG. 5 shows an example according to the example FIG. 3 based example of a hydrostatic drive 401.
  • the Nachsaugung that in the embodiment according to FIG. 4 is made possible via the third pressure medium connection, solved in an alternative way.
  • To simplify the description of the hydrostatic drive 401 reference is made at this point only to the differences from the third example according to FIG. 3 received.
  • a second throttle device 428 of the second pressure medium connection has instead of the blocking position 228b according to FIG. 3 a constructionally related residual opening position b with a residual opening cross-section A 2R .
  • the residual opening cross-section A 2R is dimensioned such that sufficient pressure medium can flow into the other piston chamber 10 via it, but no pressure buildup takes place in the latter.
  • the dimensioning is selected so that adjusts the pressure p B ⁇ 10 bar in the other piston chamber 10. This is sufficient to prevent cavitation in the other piston chamber 10 due to dynamic movement effects of the piston 4.
  • FIG. 12 shows a valve device 354 that summarizes the second throttle device 228 and the third throttle device 342.
  • the valve device 354 is also in the embodiment according to FIG. 4 installed. It is designed as a valve block with the connections L, A, X, and B1 and B2. Via the connection A, the second and third pressure medium connection 26 and 340 with the first pressure medium connection 18 according to FIG FIG. 4 connectable. Via the connection X, the load-signaling line 232 can be fluidically connected to the one piston chamber 8. Via the port B1 of the other piston chamber can be connected and via the port B2, the hydraulic pump 24 can be connected.
  • the valve device 354 summarizes in a compact manner the functions of the load pressure-dependent regeneration of pressure medium from one piston chamber 8 in the other piston chamber 10 via the second throttle device 228 and the pressure-controlled Nachsaugung in the other piston chamber 10 via the third throttle device 342 together.
  • the hydrostatic drive 401 has a fourth throttle device 450, via which an opening cross section of the pressure medium connection of the hydraulic pump 24 with the one piston chamber 8 can be controlled.
  • a further check valve 452 between the fourth throttle device 450 and the working port of the hydraulic pump 24 is provided, on the one hand to prevent the flow of pressure medium from the one piston chamber 8 to the hydraulic pump 24 and on the other hand to allow the pressure medium supply of a piston chamber 8 by the hydraulic pump 24.
  • the mentioned pressure medium connections can each be designed as a pressure medium line or pressure medium channel.
  • a hydrostatic drive with a double-acting hydraulic cylinder for moving a load wherein one of the piston chambers of the hydraulic cylinder for recuperation of particular potential energy of the load with a hydraulic machine, in particular a hydraulic motor, and / or a hydraulic accumulator is fluidically connectable.
  • the hydraulic cylinder to a second pressure medium connection, via which the other piston chamber for the regeneration of pressure medium energy with a partial volume flow of a flowing away from a piston chamber drain volume flow can be supplied.
  • a hydrostatic drive with a hydraulic cylinder for moving a load, a piston chamber with a hydraulic machine and / or a hydraulic accumulator for recuperation of hydraulic energy of the hydraulic cylinder is fluidly connected.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (14)

  1. Mécanisme d'entraînement hydrostatique comprenant un vérin hydraulique (2) destiné à déplacer, notamment à lever et/ou à abaisser une charge (FL), et comprenant une machine hydraulique (20) et/ou un accumulateur hydraulique (121) destinés à la récupération de l'énergie hydraulique du vérin hydraulique (2), notamment de l'énergie potentielle et/ou cinétique de la charge (FL), deux espaces de piston (8, 10) étant séparés fluidiquement l'un de l'autre dans le vérin hydraulique (2) par un piston (4), dont un espace de piston (8) peut être relié fluidiquement à la machine hydraulique (20) et/ou à l'accumulateur hydraulique (121) par le bais d'une première liaison de fluide sous pression (18) du mécanisme d'entraînement (301), et comprenant une deuxième liaison de fluide sous pression (26) par le biais de laquelle l'autre espace de piston (10) peut être alimenté avec un débit volumique partiel d'un débit volumique d'écoulement qui s'échappe d'un espace de piston (8), caractérisé par une troisième liaison de fluide sous pression (340) branchée en parallèle avec la deuxième liaison de fluide sous pression (26), par le biais de laquelle l'autre espace de piston (10) peut être alimenté avec un débit volumique partiel du débit volumique d'écoulement et laquelle comporte un troisième dispositif d'étranglement (342) par le biais duquel peut être commandée la troisième liaison de fluide sous pression (340), le troisième dispositif d'étranglement sous pression (342) ayant une troisième section transversale d'ouverture réglable en fonction de la pression (pB) de l'autre espace de piston (10).
  2. Mécanisme d'entraînement selon la revendication 1, comprenant un premier dispositif d'étranglement (22) ayant une première section transversale d'ouverture réglable par le biais de laquelle peut être commandée la première liaison de fluide sous pression (18).
  3. Mécanisme d'entraînement selon la revendication 1 ou 2, comprenant un deuxième dispositif d'étranglement (28 ; 228 ; 428) ayant une deuxième section transversale d'ouverture (A2), réglable en fonction de la pression (pA) dudit espace de piston (8) et par le biais de laquelle peut être commandée la deuxième liaison de fluide sous pression (26).
  4. Mécanisme d'entraînement selon la revendication 3, la deuxième section transversale d'ouverture (A2) pouvant être commandée en fermeture en fonction de la pression (pA) croissante dudit espace de piston (8) et/ou la deuxième section transversale d'ouverture (A2) pouvant être commandée en ouverture en fonction de la pression (pA) décroissante dudit espace de piston (8).
  5. Mécanisme d'entraînement selon la revendication 3 ou 4, le deuxième dispositif d'étranglement (28 ; 228 ; 428) étant chargé en direction d'une commande de fermeture de la deuxième section transversale d'ouverture (A2) avec la pression (pA) dudit espace de piston (8).
  6. Mécanisme d'entraînement selon l'une des revendications 3 à 5, comprenant un équivalent de pression bas (pAu) avec lequel le deuxième dispositif d'étranglement (28 ; 228 ; 428) est chargé en direction d'une commande d'ouverture de la deuxième section transversale d'ouverture (A2).
  7. Mécanisme d'entraînement selon la revendication 6, la deuxième section transversale d'ouverture (A2) étant commandée en ouverture de manière sensiblement constante lorsque la pression (pA) dudit espace de piston (A) est inférieure à l'équivalent de pression bas (pAu) .
  8. Mécanisme d'entraînement selon la revendication 6 ou 7, la deuxième section transversale d'ouverture (A2) pouvant être commandée en fermeture de manière sensiblement proportionnelle en fonction de la pression (pA) dudit espace de piston (8) lorsque la pression (pA) dudit espace de piston (8) devient supérieure à l'équivalent de pression bas (pAu).
  9. Mécanisme d'entraînement selon l'une des revendications 6 à 8, comprenant un équivalent de pression haut (pAo) avec lequel le deuxième dispositif d'étranglement (228 ; 428) est chargé en direction d'une commande d'ouverture de la deuxième section transversale d'ouverture (A2) et qui est supérieur à l'équivalent de pression bas (pAu) .
  10. Mécanisme d'entraînement selon la revendication 9, la pression (pA) dudit espace de piston (8) pouvant être limitée par le biais de l'équivalent de pression haut (pAo) .
  11. Mécanisme d'entraînement selon la revendication 9 ou 10, le deuxième dispositif d'étranglement (428) possédant une section transversale d'ouverture restante (A2R) lorsque la pression (pA) dudit espace de piston (8) est approximativement égale à l'équivalent de pression haut (pAo) ou supérieure à celui-ci.
  12. Mécanisme d'entraînement selon l'une des revendications précédentes, la troisième section transversale d'ouverture pouvant être commandée en fermeture en fonction de la pression (pB) croissante de l'autre espace de piston (10) et/ou la troisième section transversale d'ouverture pouvant être commandée en ouverture en fonction de la pression (pB) décroissante de l'autre espace de piston (10).
  13. Mécanisme d'entraînement selon l'une des revendications précédentes, comprenant un équivalent de pression (344) notamment réglable avec lequel le troisième dispositif d'étranglement (342) est chargé en direction d'une commande d'ouverture de la troisième section transversale d'ouverture.
  14. Mécanisme d'entraînement selon la revendication 3, comprenant un dispositif à vanne, lequel est réalisé en construction par blocs ou par plaques, et lequel possède le deuxième dispositif d'étranglement (28 ; 228 ; 428) ayant la deuxième section transversale d'ouverture (A2) qui peut être réglée en fonction de la pression (pA) dudit espace de piston (8), par le biais duquel peut être commandée la deuxième liaison de fluide sous pression (26), et lequel possède la troisième liaison de fluide sous pression (340) branchée en parallèle avec la deuxième liaison de fluide sous pression (26) par le biais de laquelle l'autre espace de piston (10) peut être alimenté avec un débit volumique partiel du débit volumique d'écoulement, et lequel possède le troisième dispositif d'étranglement (342) ayant la troisième section transversale d'ouverture réglable en fonction de la pression (pB) de l'autre espace de piston (10), par le biais de laquelle peut être commandée la troisième liaison de fluide sous pression (340) .
EP15177835.4A 2014-08-13 2015-07-22 Entrainement hydrostatique et dispositif de soupape associe Active EP2985469B1 (fr)

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DE102014216031.6A DE102014216031A1 (de) 2014-08-13 2014-08-13 Hydrostatischer Antrieb und Ventilvorrichtung dafür

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TWI730301B (zh) * 2019-03-06 2021-06-11 點晶科技股份有限公司 流體驅動裝置
DE102021210054A1 (de) 2021-09-13 2023-03-16 Robert Bosch Gesellschaft mit beschränkter Haftung Energieeffiziente elektrisch-hydraulische Steueranordnung
DE102022206501A1 (de) * 2022-06-28 2023-12-28 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulischer Antrieb und Verfahren zum regenerativen Absenken eines Elements einer Arbeitsmaschine

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JPH081202B2 (ja) * 1989-04-03 1996-01-10 株式会社豊田自動織機製作所 単動式油圧シリンダの作動回路
JPH08193601A (ja) * 1995-01-13 1996-07-30 Ckd Corp シリンダの制御回路及び制御方法
US20090288408A1 (en) * 2005-06-06 2009-11-26 Shin Caterpillar Mitsubishi Ltd. Hydraulic circuit, energy recovery device, and hydraulic circuit for work machine
JP2006336846A (ja) * 2005-06-06 2006-12-14 Shin Caterpillar Mitsubishi Ltd 流体圧回路
DE102005059238B4 (de) * 2005-12-12 2016-03-31 Linde Hydraulics Gmbh & Co. Kg Steuerventileinrichtung zur Steuerung eines Verbrauchers
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JP5257807B2 (ja) * 2006-11-14 2013-08-07 フスコ インターナショナル インコーポレイテッド 油圧システムのためのエネルギー回収及び再利用技術
DE102008034301B4 (de) * 2007-12-04 2019-02-14 Robert Bosch Gmbh Hydraulisches System mit einem verstellbaren Schnellsenkventil
DE102009037198A1 (de) * 2009-08-12 2011-02-17 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102012003320A1 (de) 2012-02-18 2013-08-22 Robert Bosch Gmbh Mobile Arbeitsmaschine mit Energierückgewinnung zum Antrieb der Motorkühlung

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EP2985469A1 (fr) 2016-02-17
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CN105370642A (zh) 2016-03-02

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