EP2157318A2 - Dispositif d'alimentation hydraulique - Google Patents

Dispositif d'alimentation hydraulique Download PDF

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Publication number
EP2157318A2
EP2157318A2 EP09165363A EP09165363A EP2157318A2 EP 2157318 A2 EP2157318 A2 EP 2157318A2 EP 09165363 A EP09165363 A EP 09165363A EP 09165363 A EP09165363 A EP 09165363A EP 2157318 A2 EP2157318 A2 EP 2157318A2
Authority
EP
European Patent Office
Prior art keywords
pressure
supply unit
fluid
valve
unit according
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.)
Withdrawn
Application number
EP09165363A
Other languages
German (de)
English (en)
Other versions
EP2157318A3 (fr
Inventor
Thomas Busold
Sven Reinbold
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2157318A2 publication Critical patent/EP2157318A2/fr
Publication of EP2157318A3 publication Critical patent/EP2157318A3/fr
Withdrawn legal-status Critical Current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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure

Definitions

  • the present invention relates to a hydraulic supply unit, as it can be used in particular in a vehicle to supply a hydraulic consumer having at least one consumption area, with pressurized fluid.
  • Such a system area is formed for example by a gas spring torsional vibration damper arrangement, which is arranged in a drive train of a vehicle and counteracts the occurrence of torsional vibrations in the drive train.
  • gas spring Torsionsschwingungsdämpferan shallen generally with a compressible fluid, so for example air, filled gas spring units, which are loaded in relative rotation between a primary side and a secondary side.
  • a compressible fluid so for example air, filled gas spring units, which are loaded in relative rotation between a primary side and a secondary side.
  • the train or shear load of a drive train then by appropriate displacement or promotion of an incompressible fluid such.
  • a hydraulic supply unit for supplying a hydraulic consumer with at least one consumable area with pressurized fluid, comprising a pressurized fluid source for providing pressurized fluid and a supply valve arrangement for selectively supplying pressurized fluid to at least one consumable area, wherein the pressurized fluid source and the supply valve arrangement are combined to form a structural unit are.
  • the elementary system areas namely the pressure fluid source on the one hand and the supply valve arrangement on the other hand, are combined to form a structural unit.
  • these very closely interacting system areas are also very close to each other and thus the transmission paths and resulting pressure losses or leaks can be kept very low.
  • the combination of these essential system areas to form a unit further makes it possible to accommodate this compact formable unit with comparatively great freedom in a vehicle.
  • the structural unit comprises a plurality of housing elements, on and / or in which components of the pressure fluid source and the supply valve arrangement are provided.
  • the source of pressurized fluid may include a pressurized fluid pump drivable by a drive motor and a pressurized fluid reservoir.
  • a pressurized fluid reservoir ensures that even spontaneous pressurized fluid requirements can be met without having to start up the generally relatively long delay pressurized fluid pump.
  • the pressure fluid pump may be designed as a planetary rotor pump.
  • the pressure fluid reservoir comprises a substantially cylindrical storage housing with a displaceable pressure fluid separating a compressible storage fluid separating piston, which is proposed according to a particularly advantageous embodiment variant that a ratio between a maximum stroke of the separating piston and an inner transverse dimension of the storage enclosure at least 1 amounts to.
  • a ratio between a maximum stroke of the separating piston and an inner transverse dimension of the storage enclosure at least 1 amounts to.
  • the supply valve arrangement in association with each optionally be supplied with pressurized fluid consumption by a fluid control pressure to be adjusted main control valve for establishing and interrupting the connection between a main pressure line and a consumption area and a standing under the control of a control device pilot valve Applying the fluid control pressure to a respective associated main control valve comprises.
  • a pressure reducer be provided for feeding a pilot valve with an inlet pressure below the fluid pressure in the main pressure line ,
  • Each main control valve may include a main control valve spool having two valve closure regions, and it may be further provided that all main control valve spools are slidably received in a common main control valve housing member.
  • each main control valve spool is slidably received in a valve spool opening formed in the main control valve housing member and provided with at least one circumferential groove in an outer peripheral area.
  • each pilot valve comprises a pilot valve slide with two valve closure regions, wherein all pilot valve slide can be slidably received in a common pilot valve housing element.
  • the pressure reducer may include a pressure reducing valve spool having a valve closure portion.
  • the pressure reducing valve spool is slidably received in the pilot valve housing.
  • the pressure fluid pump is provided substantially in a main housing element, wherein it is preferably further provided that the pressure fluid reservoir is supported on the main housing element.
  • the main control valve housing member and the pilot valve housing member are preferably supported on the main housing member.
  • the present invention further relates to a hydraulic system comprising a hydraulic consumer to be supplied with pressurized fluid having at least one consumption area and a hydraulic supply unit according to the invention.
  • Such a hydraulic consumer for example, have two consumption ranges. This can be z. B. be the case when the hydraulic consumer comprises a pressure fluid torsional vibration damper assembly.
  • a hydraulic supply unit 10 can be seen, which can be used in a vehicle to supply pressurized, substantially incompressible fluid, for example oil, to a hydraulic consumer.
  • a hydraulic consumer may, for example, be a gas-spring torsional vibration damper arrangement which, with its system areas for providing damping functionality both in the direction of pull and in the direction of thrust, provides two consumption areas.
  • the inventively constructed hydraulic supply unit 10 is basically constructed as a structural unit, so that this unit can be easily integrated into a vehicle.
  • this hydraulic supply unit comprises a main housing element 12, which may be constructed, for example, of metal and approximately cube-like and in which essentially a pressure fluid pump 14, which will be explained in more detail below, may be provided at a pressure fluid source generally designated 16.
  • the pressurized fluid source 16 further includes a pressure accumulator 18 carried on the main housing member 12.
  • the hydraulic supply unit 10 according to the invention comprises a pilot control valve housing element 10 and a main control valve housing element 22 which are to be fixed to two mutually orthogonal faces of the main housing member 12 with interposition of respective plate-like sealing elements 24 by screw or the like.
  • a drive motor 28 is provided for driving the pressure fluid pump 14 at this.
  • the hydraulic supply unit 10 comprises a fluid container 30, which is connected via a line 32 in connection with a side housing element 34, via which the pressure fluid pump 14 receives fluid and then discharges under pressure, in particular in the direction of pressure accumulator 18.
  • the volume of the fluid container can be designed so that, even taking into account the delivery capacity of the pressure fluid pump 14, the maximum absorption volume of a hydraulic consumer of fluid can be kept ready.
  • the maximum fill level should be about 80 to 90% of the height of the fluid container 30. The remaining free space is used for the separation of air bubbles. If from pressurized fluid consuming system areas fluid is fed back, which may be in the form of leakage flows, return lines below the lowest fluid level should open into the fluid container 30 to avoid the entrainment of air when flowing in fluid.
  • the fluid container 30 may be provided with a filling screen and a vent.
  • the main housing element 12 further comprises an electrical connection region 15, via which the pressure fluid pump 14 can be connected to a drive device.
  • the fluid container 30 lies above the main housing element 12 and thus also above the pressure fluid pump 14 received substantially therein, so that this fluid flows out of the housing Fluid container 30 does not have to suck, but under gravity utilization of the fluid from the fluid container 30 in the direction of the side housing member 34 and can flow over this to the pressure fluid pump 14.
  • the fluid reservoir 30 may be the only reservoir for the supply of pressurized fluid.
  • this fluid container 30 can be replaced by a reservoir provided, for example, by a transmission sump, or to be supplied with fluid from this via a further pump, for example the transmission oil pump, which in turn can then be delivered in the direction of the pressure fluid pump 14.
  • the Fig. 5 shows in a circuit diagram-like representation of the structure of the hydraulic supply unit 10 according to the invention with the pressure fluid pump 14 and this driving drive motor 28.
  • This can be designed as a permanently excited DC breast motor whose speed can be adjusted by varying the voltage applied thereto or medium voltage.
  • a brushless permanent magnet motor is conceivable, which is electrically commutated.
  • the commutation and detection of the rotational position of the rotor thereof can be done electronically by block commutation with Hall sensors, by sensorless block commutation or by sinusoidal commutation.
  • the drive motor 28 Since the pressure accumulator 18 is provided in the hydraulic supply system according to the invention, the drive motor 28 therefore only needs to be operated for a relatively short time in order to charge the pressure accumulator 18 in case of need, the drive motor 28 can in principle be slightly undersized, so that it can also be operated briefly with overload , which makes the assembly of the invention easier and cheaper.
  • the pressure fluid pump 14 Via a suction filter 36 with, for example, parallel-connected check valve 38, the pressure fluid pump 14 receives fluid from a reservoir 40, for example, as already explained above Fluid tank 30 or a transmission oil sump or the like.
  • the pressure fluid pump 14, for example, via the flow channels formed in the main housing member 12 from the pressure fluid in the direction of a main pressure line 42, with which also the pressure accumulator 18 and a pressure sensor 44 is in communication.
  • a non-return valve 46 is assigned to the output side thereof.
  • a pressure relief valve 48 ensures that when the pressure in the main pressure line 42 has reached a predetermined operating pressure, with continued operation of the pressure fluid pump 14, an excessive pressure increase can not take place, but still promoted, but basically no longer needed fluid back to the reservoir 40th can flow back.
  • the pressure sensor 44 may be a combined pressure / temperature sensor, the measuring range should not be too large to obtain a high resolution for targeted control of the drive motor 28 by a drive device.
  • a pressure filter may be provided on the output side of the pressure fluid pump 14, as described with reference to FIG Fig. 1 and 4 recognizable pressure filter 52 is illustrated. Also, this pressure filter 52 may be arranged in corresponding flow spaces of the main housing member 12. In this pressure filter 52, a bypass valve may be integrated or be connected in parallel thereto, in order to avoid, in particular due to high toughness at low temperature resulting pressure differences in the range of this pressure filter.
  • a hydraulic load 50 for example, the previously mentioned gas spring Torsionsschwingungsdämpferan extract with its two consumption areas 54, 56, to supply the principle with pressurized fluid are.
  • Each of these two consumption areas 54, 56 is assigned to a pilot control valve 58 or 60, for example, which is to be actuated electromagnetically by a drive device, and to a main control valve 62 or 64.
  • Each of the main control valves 62, 64 receives a fluid control pressure from the associated pilot valve 58, 50.
  • the fluid pressure prevailing in the main pressure line 42 is then possibly applied in a reduced manner to the associated consumption area 54, 56.
  • a pressure reducer 66 is provided via which fluid is branched from the main pressure line 42 and at a substantially constant and under pressure in the Main pressure line 42 lying fluid pressure to the pilot valves 58, 60 is performed.
  • this inlet pressure should preferably be below a level below the lower threshold pressure of the main pressure line 42, reaching it after appropriate sensing by the pressure sensor 44 to energize the drive motor 28 and thus to increase the fluid pressure in the main pressure line 42 until reaching the normal operating pressure , d. H. an upper pressure threshold leads.
  • the control of the two pilot valves 58, 60 takes place with the already mentioned control device by utilizing the example of position sensors detected relative positioning of a primary side and a secondary side of a gas spring Torsionsschwingungsdämpferan für or the like. If a fluid control pressure is to be applied to the main control valves 62, 64, the pilot valves 58, 60 are energized. In the non-energized state, a line leading to the main control valves 62 and 64, respectively, is in communication with the reservoir 40, while when energized, the input pressure provided via the pressure reducer 64 is forwarded, if necessary, in a reduced form and leads to a corresponding adjustment of the main control valves 62, 64.
  • Fig. 6 to 9 show an example of an embodiment of a pressure fluid pump 14, here in the form of a planetary rotor pump. It should be noted here that other configurations, for example as a vane pump or the like, can be selected.
  • the planetary rotor pump or pressure fluid pump 14 comprises a shaft 68 mounted in the main housing element 12 by a bearing 66, for example a permeable sliding bearing, which is mounted in its free end region via a further slide bearing 70 in a housing cover 72.
  • a bearing 66 for example a permeable sliding bearing
  • a fluid-tight completion of the shaft 68 with respect to the main housing member 12 is achieved.
  • a fluid-tight seal between the main housing member 12 and the housing cover 73 is achieved by a sealing ring 78.
  • a drive shaft 80 of the drive motor 28 may be coupled to the shaft 68 for rotation by positive locking engagement when the drive motor 28 is secured to the main housing member 12 by, for example, bolting.
  • a rotor or sun gear 82 is rotatably supported on the shaft 68, for example, by a spline toothing, so that this sun gear 82 rotates with the shaft 68 about the axis of rotation A1.
  • a housing recess 84 which is basically circular, the central axis A2 is offset to the axis A1, however, is a ring gear 86th rotatably received.
  • a plurality of substantially cylinder-shaped planetary gears 88 is a plurality of substantially cylinder-shaped planetary gears 88.
  • the eccentric arrangement of the two shafts A1 and A2 produces a circumferential rotation 90 in rotation, which via a formed on an end face of the recess 84 kidney-shaped inlet opening 92nd during rotation of the sun gear 82 absorbs fluid and then emits it during rotation via an outlet opening 94.
  • kidney-shaped openings 92, 94 which are provided in the region of the bottom of the recess 84, corresponding blind openings in the housing cover 72 are opposite, to load the different wheels 82, 86 and 88 on both axial sides substantially equal.
  • the various wheels 82, 86, 88 of the pressure fluid pump 14 may be constructed of sintered steel, for example, while the main housing member 12 may be constructed of, for example, aluminum or to avoid thermally induced change in the gap dimension also made of steel.
  • pilot valves 58, 60 arranged in the pilot valve housing element 20 and also the pressure reducer 66 will be described.
  • Fig. 10 a sectional view of the pilot valve housing member 20 in the region of the pressure reducer 66 and also of the pressure sensor 44.
  • line section 96 of the pressure sensor 44 is in communication with the main pressure line 42nd
  • the pressure reducer 66 includes a pressure reducing valve spool 98, which in an associated opening 100 in the pilot valve housing element 20th slidably received. By a closing element 102 is supported on a biasing spring 104 of the pressure reducing valve 98 in a in the Fig. 10 biased illustrated end position.
  • the pressure reducing valve spool 98 has a cylinder-like valve closure region 106, which produces a more or less strong connection between two conduit regions 108, 110, depending on the axial positioning of the pressure-reducing valve spool 98. In the in Fig. 10 shown state, this connection formed by a gap 112 is maximum.
  • the line section 108 communicates with the main pressure line 42.
  • the line section 110 leads to the two pilot valves 58, 60.
  • a line section 116 leading to an axial end 114 is also in communication with the line leading to the pilot valves 58, 60 and serves for sensing of the prevailing in this line pressure. If this increases, the axial end 114 of the pressure reducing valve spool 98 is acted upon by this pressure reinforced and the pressure reducing valve spool 98 against the biasing action of the spring 104 is displaced.
  • the width of the gap-like intermediate space 112 is reduced, so that the line section 110 is increasingly disconnected from the line section 108, ie the main pressure line 42, and thus the fluid pressure in the line sections 110, 116, ie the line leading to the pilot control valves 58, 60, decreases .
  • the biasing action of the biasing spring 104 By adjusting the biasing action of the biasing spring 104, the pressure level to be applied to the pilot valves 58, 60 can be adjusted. Via conduit sections 118, 120, a return of fluid leaks, for example, to the reservoir 40 can be achieved.
  • Each of these pilot valves 58, 60 includes a generally designated 120 solenoid assembly having a coil 122, the excitation of which leads to the displacement of an anchor portion 124. This acts on a valve spool 126 against the biasing action of a biasing spring 128. In non-energized coil 122, the valve spool 126 of each pilot valve 58, 60 in the in Fig. 11 recognizable positioning shifted to the rightmost position.
  • the valve spool 126 comprises two cylinder-shaped and displaceable in an opening 130 valve end regions 132, 134. In the in Fig. 11 recognizable state, the valve closure portion 134, a connection between two line sections 136, 138 free.
  • the line section 136 leads to the reservoir 40, is therefore generally depressurized.
  • the conduit section 138 leads to the main control valves 62 and 64, respectively, to apply a fluid control pressure thereto.
  • the valve closure portion 132 interrupts in the in Fig. 11 state shown the connection between the line section 138 and a line section 140, via which a connection between the respective pilot valve 58, 60 and the pressure reducer 66, so for example the line section 110 and 118 is made. Is against the biasing action of the biasing spring 128 by energizing the solenoid assembly 120 of the valve slide 126 in the Fig.
  • connection between the line sections 136, 138 decreases, while when this connection is completely interrupted and the valve spool 126 is moved further, the connection between the line section 140, so the input pressure of a respective pilot valve 58 and 60th , and the line section 138, so the leading to a respective main control valve 62 and 64 line increases.
  • the input pressure at the conduit portion 140 can be more or less applied as a fluid control pressure to a respective associated main control valve.
  • an electrical connection region 146 via which in particular the two pilot valves 58, 50 can be brought into drive connection with the drive device.
  • the Fig. 13 and 14 show the structure of the main control valves 62, 64 and their positioning in the main control valve housing element 22. This is in the Fig. 13 viewed from its to be connected to the main housing member 12 end face ago.
  • Each of the main control valves 62, 64 includes, as in section Fig. 14 discernible, a valve spool 150 which is slidably received in an opening 152 in the main control valve housing member 22. This opening 152 is closed by a closure element 154, on which a biasing spring 156 is supported. This biasing spring 156 biases the valve spool 150 in the in the Fig. 14 recognizable positioning ago, in which acts on this no fluid control pressure.
  • An end portion 158 of the valve spool 150 remote from the biasing spring 156 is connected via a conduit portion 160 in communication with a conduit which leads from the associated pilot valve and through which the fluid control pressure is applied.
  • This fluid control pressure acts on the axial end region 158 of the valve slide 150 counter to the biasing action of the biasing spring 156 and shifts the valve spool 150 starting from the in accordance with the size of the applied Fuid Kunststoffbuchs Fig. 15 recognizable positioning to the left.
  • the valve spool 150 has two valve closure regions 162, 164. These are guided displaceably in the opening 152. In the in Fig. 14 As shown, the valve closure region 162 communicates between a conduit section 166 and a housing Line section 168 to. The conduit section 166 is in communication with the non-pressurized reservoir 40. The conduit section 168 connects to the respective expendable area 54 and 56, respectively.
  • the valve closure region 164 interrupts in the in Fig. 14 state shown the connection between the line section 168 and another line section 170 which is in communication with the main pressure line 42.
  • a further line section 172 can be seen in the main control valve housing element 122, which communicates with the line section 166 and likewise has a connection to the reservoir 40.
  • the switching characteristics can be influenced by configuring the control edges with which the valve termination regions can each interrupt a connection of two line sections.
  • a linear valve characteristic can be generated.
  • a rounded or chamfered transition at the end of a respective valve closure region may contribute to a correspondingly bent valve characteristic.
  • a progressive characteristic curve can be obtained, which is a very fine setting of the pressures to be passed through a respective valve.
  • the apertures receiving the valve spools in their regions in which they cooperate with the valve closure regions may contribute by chamfering or corresponding design to produce a defined, for example, progressive valve characteristic.
  • valve spool or the pressure reducing valve spool may be constructed of aluminum, as well as the two housing elements 20, 22. Furthermore, the valve spool can be hard anodized after turning.
  • FIGS. 15 and 16 show an embodiment of the pressure accumulator 18.
  • This can be constructed with a pressure accumulator housing 180 which has a substantially cylindrical, for example circular cylindrical, peripheral wall 182, on which a closing element 184 is fixed.
  • a separating piston 186 in the direction of the longitudinal axis L of the housing 180 is displaceable.
  • the separating piston 186 separates in the representation of Fig. 15 maximum volume V, in which one Gas, for example air, is arranged, of the pressure fluid contained and connected via a line section 188 to the main pressure line 42 volume.
  • the separating piston 186 is guided in the housing 180 defined by two guide rings 188, 190 located in its axial end region.
  • a sealing ring 192 provides a fluid-tight seal of the volume V with respect to the volume containing pressurized fluid.
  • the separating piston 86 so at maximum expansion of the gas in the volume V in the in Fig. 15 and in Fig. 16 is recognizable positioning in contact with a further closing element 194, gradually escapes the gas by overcoming the sealing member 192, a further ring-like sealing member 196 is provided at the axial end of the separating piston 186.
  • the ratio of the maximum stroke of the separating piston 186 which also essentially corresponds to the length of the circumferential wall 182 or pressure accumulator 18 in the direction of the longitudinal axis L, to be at least 1 to the diameter or to the transverse inner dimension should, but is preferably larger. If correspondingly high pressures can not be stored, that is, if a design for high pressures is not required, then it may be advantageous to design this ratio smaller than 1, ie to form the pressure reservoir 18 with a comparatively large transverse dimension and comparatively short length, so that at the removal of a predetermined pressure fluid volume of the separating piston 186 only has to move comparatively little and thus lower friction losses will occur.
  • a hydraulic supply unit constructed in accordance with the invention which has combined to form a structural unit all relevant system areas which are required to provide and store pressurized fluid even under comparatively high pressure and, if necessary, to deliver it to the consumption areas of a hydraulic consumer.
  • the unit according to the invention can operate completely autonomously, but can advantageously be connected to a fluid reservoir, for example a transmission oil sump, in order to ensure that pressurized fluid can be repeatedly provided over longer periods of operation, with used pressurized fluid or leakage flows then being returned to the closed circuit can.

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  • Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP09165363.4A 2008-08-18 2009-07-14 Dispositif d'alimentation hydraulique Withdrawn EP2157318A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810041305 DE102008041305A1 (de) 2008-08-18 2008-08-18 Hydraulikversorgungseinheit

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Publication number Priority date Publication date Assignee Title
WO2012072346A1 (fr) * 2010-11-29 2012-06-07 Robert Bosch Gmbh Système d'injection de carburant pour moteur à combustion interne

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017220090A1 (de) * 2017-11-10 2019-05-16 Zf Friedrichshafen Ag Druckmittelversorgungseinrichtung

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Publication number Priority date Publication date Assignee Title
DE3530019A1 (de) * 1984-12-18 1986-06-26 Shoketsu Kinzoku Kogyo K.K., Tokio/Tokyo Richtventilanordnung
DE4234013A1 (de) * 1992-10-09 1994-04-14 Teves Gmbh Alfred Hydraulikaggregat für schlupfgeregelte Bremsanlagen
DE19725092A1 (de) * 1997-06-13 1998-12-17 Itt Mfg Enterprises Inc Hydraulisches Aggregat

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
DE3530019A1 (de) * 1984-12-18 1986-06-26 Shoketsu Kinzoku Kogyo K.K., Tokio/Tokyo Richtventilanordnung
DE4234013A1 (de) * 1992-10-09 1994-04-14 Teves Gmbh Alfred Hydraulikaggregat für schlupfgeregelte Bremsanlagen
DE19725092A1 (de) * 1997-06-13 1998-12-17 Itt Mfg Enterprises Inc Hydraulisches Aggregat

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012072346A1 (fr) * 2010-11-29 2012-06-07 Robert Bosch Gmbh Système d'injection de carburant pour moteur à combustion interne

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EP2157318A3 (fr) 2014-01-22

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