EP1309801B1 - Ventil - Google Patents

Ventil Download PDF

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Publication number
EP1309801B1
EP1309801B1 EP01974121A EP01974121A EP1309801B1 EP 1309801 B1 EP1309801 B1 EP 1309801B1 EP 01974121 A EP01974121 A EP 01974121A EP 01974121 A EP01974121 A EP 01974121A EP 1309801 B1 EP1309801 B1 EP 1309801B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
connection
consumer
flow regulator
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.)
Expired - Lifetime
Application number
EP01974121A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1309801A2 (de
Inventor
Alois Hoffmann
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP1309801A2 publication Critical patent/EP1309801A2/de
Application granted granted Critical
Publication of EP1309801B1 publication Critical patent/EP1309801B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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
    • F15B2211/7052—Single-acting output members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2594—Choke
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7792—Movable deflector or choke

Definitions

  • the invention relates to a valve with the features of the preamble of Claim 1.
  • valves are regularly used in so-called hydraulic Load-sensing systems or controls are used and work there in the manner of a pressure compensator that uses an unneeded pump flow return to the tank with a low pressure drop.
  • a pressure compensator that uses an unneeded pump flow return to the tank with a low pressure drop.
  • Overriding the load sensing system is the consumer connection to relieve the tank.
  • the relief in this regard is nowadays implemented inexpensively by an aperture control, the Aperture is preferably integrated directly in the pressure compensator or separately is used in a control block, the part of the load-sensing control is.
  • a generic valve is known with at least a pump, a tank and a consumer connection and with a valve piston which can be moved within the valve housing and which at least one blocking position the pump connection from the tank connection separates and which interacts with an energy store, whereby by means of a Control device on between the consumer connection and the tank connection adjusting fluid flow can be controlled, the control device consists of a fluid flow controller integrated in the valve piston and wherein the fluid flow regulator has a flow regulator piston, which in the valve piston is guided longitudinally and which is against another Lift mechanism supports.
  • the known solution is required for implementation their function a variety of components, so that the manufacturing costs for the known valve are correspondingly high and otherwise required known solution thereby a relatively large amount of space.
  • the object of the invention based on further improving the known valves in that they the disadvantages described, especially when used in so-called load-sensing systems, do not have. Furthermore, the valve should be inexpensive can be realized and take up a small amount of space.
  • a pertinent one Task solves a valve with the features of the claim 1 in its entirety.
  • the flow control piston has a fluid channel which is at least in one Displacement position of the flow control piston in a fluid channel of the valve piston opens out, at least in a displacement position of the valve piston opens into a separate tank connection in the valve housing, which from the tank connection that can be connected to the pump connection is separated it is possible, in contrast to the known valve solutions with the orifice construction the volume flow to the consumer regardless of the load reduce a constant value so that a proportional load-independent Control is realized.
  • the disadvantages described in the prior art Technology, especially in the form of a slowdown of the consumer thus definitely excluded.
  • the solution according to the invention with Fluid flow controller can be implemented inexpensively and through the integration of the fluid flow controller in the valve housing is a space-saving installation possible in the valve itself. Since the valve of the invention with little Building components, is also a functionally reliable Operation guaranteed by the entire load sensing system benefits.
  • the valve shown in longitudinal section in FIG. 1 has a pump connection 10 on, namely at the front end of a valve housing 12, which is designed in the manner of a screw-in cartridge, so as to Control blocks or the like to be determined for later use.
  • the configuration in the form of an installation set or the like is also possible.
  • the valve housing has at its end facing the pump connection 10 12 two diametrically opposite first tank connections 14 on.
  • a further separate tank connection 16 is arranged on the left half of the figure, whose free opening cross-section is smaller than the corresponding diameter range of the first tank connections 14 introduced another transverse bore in the valve housing 12, which as Consumer connection 18 is used.
  • the tank connections 14 and 16 are also preferably formed from transverse bores in the valve housing 12.
  • the mentioned connections 14, 16 and 18 run essentially transverse to the longitudinal axis 20 of the valve housing 12.
  • the pump connection 10 however, along the longitudinal axis 20 of the valve housing 12 is on this arranged at the front.
  • a valve piston 22 is arranged to be longitudinally displaceable in the valve housing 12, the outer circumference in the usual and therefore not described in detail Way is provided with pressure relief channels. In one of his shown In any case, he separates blocking positions as shown in FIG. 1 the pump connection 10 from the tank connection 14. Furthermore, the valve piston acts 22 together with an energy accumulator 24, wherein by means of a Whole with 26 designated control device between the consumer connection 18 and the tank port 14 fluid flow is controllable.
  • the mentioned control device 26 exists in particular from a fluid flow controller which is integrated in the valve piston 12 and in terms of its structure and function below will be explained in more detail.
  • the fluid flow controller mentioned has a flow control piston 28, which is guided longitudinally in the valve piston 22, the inner circumference of the valve piston 22 the outer circumference of the flow control piston 28 includes.
  • the current regulator piston 28 is in turn supported on another Energy store 30 from, the direction of action against the first energy store 24 is directed.
  • the flow regulator piston 28 has a fluid channel 32 which at least in a displacement position of the current regulator piston 28 according to the representation according to FIG. 1 in a fluid channel 34 of the valve piston 22 opens, the shift position shown in Figure 1 again a fluid-carrying Connection to the separate tank connection 16 in the valve housing 12 manufactures.
  • the valve piston 22 separates in each displacement position the first tank connections 14 from the further separate tank connection 16th
  • the fluid channel 32 of the flow control piston 28 is on its the consumer connection 18 facing side can be closed by a control piston 36, in the direction of this closed position via the first energy accumulator 24 is held.
  • the fluid channel has at its end 32 via a constriction and opens out, as shown in FIG shows, with a reduced cross-section on the front outside.
  • the one addressed Control piston 36 has a spherical cap 38, which is in is designed like a hemisphere and with its curved front Engagement surface for the fluid-guiding engagement in the fluid channel 32 of the Current regulator piston 28 is provided. In the illustration shown and in any other switch position, the calotte 38 leaves the mentioned free End of the fluid channel 32 with its reduced cross section for one Fluid passage free.
  • Dome 38 arranged a flange-like ring widening 40 on which with one free end supports the compression spring that supports the first Lift mechanism 24 forms.
  • the other free end of the compression spring as an energy store 24 is in contact with an end plug 42, which on the Pump connection 10 opposite end in the valve housing 12 screwed in and fixed in this way.
  • the control piston 36 has on its an end surface 44 facing the end plug 42 on, but in the normal operating state of the valve, an axial distance seen in the longitudinal direction of the longitudinal axis 20 to the end plug 42 complies.
  • the flow control piston 28 is guided inside the valve piston 22 for this purpose has a cylindrical inner recess, with a manufactured one Fluid connection between the separate tank connection 16, the Fluid channel 34 and the fluid channel 32 the upper front ends of Valve piston 22 and flow regulator piston 28 essentially flat in one Complete the plane with one another, which runs transverse to the longitudinal axis 20.
  • This switching arrangement has the lower free end of the flow regulator piston 28 such an axial distance from the lower receiving floor of the valve piston 22 on that along a radial shoulder of the flow control piston 28 this is flush with the upper edge of that part of the fluid channel 34 completes, which faces the interior of the valve piston 22.
  • the opposite side of the fluid channel 34 widens in an annular recess 46 which is essentially flush with its upper edge in the circuit diagram shown in Figure 1 with the separate tank connection 16 completes. Furthermore, the lower free end is further Energy storage 30 in the form of the compression spring in a bottom inner recess of the valve piston 22 and supported in this way.
  • the consumer connection 18 opens into a valve chamber 48 of the valve housing 12, that of the control piston 36 and the first energy accumulator 24 is reached.
  • the valve housing 12 has for the valve piston 22 on its side facing the valve chamber 48 a stop surface 50, for example formed by the use of no closer snap ring shown. The valve piston 22 is thus free in the viewing direction seen on the Fig.1 down towards the pump connection 10 to move and in the opposite direction is the travel path limited.
  • the one also called load connection is against the effect of Energy storage 24 and 30 pushed back the cap 38 as a closing part and / or the flow regulator piston 28 as seen in the direction of FIG. 1 move downward within the valve piston 22 so that the fluid channel 32 is fully released.
  • the arrangement mentioned can be adjust in such a way that the volume flow to the consumer is independent of the load can be reduced by a constant value, so that a proportional load-independent control also possible in the event of leaks is.
  • Fig.2 shows a basic circuit concept of a So-called.
  • Load-sensing systems wherein in the embodiment according to the Fig.2 as a hydraulic pump, a constant pump 52 is used. Instead of such constant pumps can also be variable pumps (not shown) can be used accordingly.
  • the load sensing mentioned should serve to achieve an optimized energy utilization, the load pressure returned to a regulator in the form of the valve therefor is used, for example, the hydraulically offered performance via the constant pump 52 and from a consumer, here in the form of a hydraulic working cylinder 54, demanded performance on each other vote.
  • Control throttle or control orifice 56 can be the consumer volume flow vary and therefore operate the working cylinder 54.
  • the consumer flow results from the free throttle opening cross-section Q and a pressure difference ⁇ p at the throttle 56, measured at the tapping points 58 in front of and behind the throttle 56.
  • the valve piston 22 has the function of a type of pressure compensator, the flow regulator piston 28, as part of the control device 26, reducing the volume flow to the consumer 54 by a constant value in the event of leakages in the hydraulic consumer circuit 62, regardless of the load.
  • the difference ⁇ p measured between the two tapping points 58, is therefore predetermined by the spring force of the energy accumulator 24, which acts on the pressure compensator in the form of the valve piston 22, and is kept constant via the pressure compensator control.
  • ⁇ p Spring force of the energy accumulator 24
  • Valve piston surface of the valve piston 22 Constant
  • the working cylinder 54 is in opposite Relieved direction, must be the related load counteracted in the sense of a constant load and the constant pump 52, the rest of the tank 68 through a pressure relief valve 60 is secured, pumps now directly over the released Connection in the first tank connections 14, in which case the valve piston 22 as a pressure compensator in a correspondingly raised travel position withdrawn in the direction of the consumer connection 18 (cf. Fig.1).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Fluid Pressure (AREA)
  • Temperature-Responsive Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
EP01974121A 2000-08-16 2001-08-07 Ventil Expired - Lifetime EP1309801B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10039936 2000-08-16
DE10039936A DE10039936A1 (de) 2000-08-16 2000-08-16 Ventil
PCT/EP2001/009083 WO2002014696A2 (de) 2000-08-16 2001-08-07 Ventil

Publications (2)

Publication Number Publication Date
EP1309801A2 EP1309801A2 (de) 2003-05-14
EP1309801B1 true EP1309801B1 (de) 2004-02-25

Family

ID=7652555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01974121A Expired - Lifetime EP1309801B1 (de) 2000-08-16 2001-08-07 Ventil

Country Status (6)

Country Link
US (1) US6799599B2 (ja)
EP (1) EP1309801B1 (ja)
JP (1) JP2004506852A (ja)
AT (1) ATE260415T1 (ja)
DE (2) DE10039936A1 (ja)
WO (1) WO2002014696A2 (ja)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009049548A1 (de) * 2009-10-16 2011-04-21 Hydac Fluidtechnik Gmbh Ventilanordnung
DE102012015356A1 (de) * 2012-08-03 2014-05-15 Hydac Fluidtechnik Gmbh Ventil, insbesondere vorgesteuertes Proportional-Wegesitzventil
DE102012015354A1 (de) 2012-08-03 2014-05-15 Hydac Fluidtechnik Gmbh Ventil, insbesondere vorgesteuertes Proportional-Wegesitzventil
EP2711560B1 (de) * 2012-09-21 2019-06-12 HAWE Hydraulik SE Hydraulikantrieb für ein hydraulisch betätigbares Werkzeug
CN103912536B (zh) * 2014-04-01 2016-03-02 嘉善海力达工具有限公司 一种反馈补偿式液压卸荷阀

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1108996B (de) * 1959-03-03 1961-06-15 Teves Kg Alfred Steuerung fuer Druckmittelverbraucher
DE2500863A1 (de) * 1975-01-10 1976-07-15 Eaton Gmbh Hydraulische servoanlage fuer mobile arbeitsmaschinen, insbesondere hublader
US4240457A (en) * 1978-03-15 1980-12-23 Caterpillar Tractor Co. Variable flow control valve for steering systems of articulated vehicles
US4921547A (en) * 1989-07-26 1990-05-01 Vickers Incorporated Proportional priority flow regulator
JPH09142319A (ja) * 1995-11-24 1997-06-03 Toyoda Mach Works Ltd 動力舵取装置における流量制御装置
DE29713293U1 (de) * 1997-07-25 1997-10-23 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil
DE19851553B4 (de) * 1998-03-19 2008-03-20 Linde Material Handling Gmbh Steuerventil

Also Published As

Publication number Publication date
EP1309801A2 (de) 2003-05-14
DE10039936A1 (de) 2002-03-07
WO2002014696A3 (de) 2002-07-18
US20030178060A1 (en) 2003-09-25
JP2004506852A (ja) 2004-03-04
WO2002014696A2 (de) 2002-02-21
ATE260415T1 (de) 2004-03-15
US6799599B2 (en) 2004-10-05
DE50101569D1 (de) 2004-04-01

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