US3924655A - Hydraulic control arrangement - Google Patents

Hydraulic control arrangement Download PDF

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Publication number
US3924655A
US3924655A US434343A US43434374A US3924655A US 3924655 A US3924655 A US 3924655A US 434343 A US434343 A US 434343A US 43434374 A US43434374 A US 43434374A US 3924655 A US3924655 A US 3924655A
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US
United States
Prior art keywords
control
passage means
fluid
throttle
inlet
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
US434343A
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English (en)
Inventor
Gunther Schwerin
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of US3924655A publication Critical patent/US3924655A/en
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Expired - Lifetime legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]
    • 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
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass
    • Y10T137/87185—Controlled by supply or exhaust valve

Definitions

  • ABSTRACT Inventor Giillthel' Schwerin, Mbglingen, A hydraulic control arrangement provided with a con- Germany trol valve having a spool movable between a neutral [73] Assignee Robert Bosch GmbH German position which closes atleast one conduit leading to a y consumer device and two working positions, in one of Flled: Jan. 17, 1974 which it connects the conduit with a fluid inlet passage 21 A I.
  • the hydraulic control arrangement includes a switch valve communicating with the [30] Foreign Application Priority Data fluid inlet and the fluid outlet of the arrangement and Jan. 24, 1973 Germany 2303286 having a valve member biased y a Spring to a PQSitiOH in which flow of fluid from the inlet to the outlet 52 US. (:1 137/596.13; 137/625.69 through the Switch valve is prevented The posit-ion of [51 Int.
  • valve member is further controlled y a p of [58 Field of Search 60/468, 494; 91/451; throttles arranged in a Control Conduit communicating 137/62569 59612 596 13 with the switch valve and arranged and constructed in such a manner that undesirable pressure increases [56] Refe Cit d during fine regulation of fluid flow passing through the UNITED STATES PATENTS control valve to the consumer device are prevented.
  • the present invention relates to a hydraulic control arrangement with a control valve for controlling flow of fluid to a consumer device.
  • the control valve has a control member which in a neutral position closes at least one conduit leading to a consumer device, whereas in two working positions of the control member the conduit is selectively connectedwith a fluid inlet or a fluid return passage.
  • the arrangement includes further a switch valve arranged to permit the pressure fluid fed into the inlet of the arrangement to pass directly into the fluid outlet and a control passage coordinated with the switch valve.
  • Flow of fluid through the control passage is controlled by the control member of the control valve and a throttle is arranged in the control passage which produces a pressure difference resulting in a force acting on the valve member of the switch valve against the force of a spring biasing the valve member of the switch valve to a position preventing direct flow from the inlet to the outlet through the switch valve.
  • a control arrangement of the aforementioned kind is known in the art in which the positionof thevvalve member of the switch .valve is hydraulically controlled.
  • the control member of the control valve is in form of a spool movable in axial direction and provided with a pluralityiof sections or piston portions formed with cutouts of gradually varying cross section for fine adjustment of the flow of fluid passing to the consumer device and the flow of fluid passing through the control passage of the arrangement.
  • this known arrangement doesnot permit a satisfactory fine control of the aforementioned fluid streams. The reason for.
  • tion mainly comprises switch valve means communicating with the fluid inlet and the fluidoutletof. thearrangement and having a valve member movablebetween an open position permitting flow of fluidfrom 2 the inlet to the outlet through the switch valve means and a closed position preventing such flow, and spring means biasing the valve member to the closed position, first control passage means communicating with the A inlet and the switch valve and connected in parallel to the latter so that fluid passing through the first control passage acts on the valve member in the same direction as the spring means, second control passage means communicating at one end with the first control passage means, a first throttle in said first control passage means upstream of said one end of said second control passage means, a second throttle in said first control passage means upstream of the first throttle, return flow passage means communicating at one end with the outlet and adapted to communicate at the other end with the other end of the second control passage means, inlet passage means communicating at one end with the first control passage means between the first and the second throttle therein, and control valve means having a control member movable between a neutral position in which it closes
  • An additional advantage of the hydraulic control arrangement according to the present invention is that it can be manufactured at reasonable cost and that it can be incorporated into known hydraulic controlarrange merits of the prior art without too great difficulties.
  • FIG. 1 is a schematic partially sectioned view of the hydraulic control arrangement according to the present invention
  • FIG. 2 is a diagram illustrating the pressure variations independence on the position of the control member of the control valve for different pressures in the consumerdevice in a control arrangement according to the prior art',
  • FIG. 3 is a diagram illustrating theamount of fluid flowing through the arrangement in dependence on the position of the control member for different pressures in the donsumer device in an arrangement according to the prior art
  • FIG. 4 is a diagram similar to FIG. 2 for the control arrangement according to the present invention.
  • FIG. 5 is a diagram similar to FIG. 3 for a control arrangement according to the present invention.
  • the hydraulic control arrangement illustrated in FIG. 1 comprises a connecting plate 11, a control valve 12 and an end plate 13, arranged in abutting relationship as shown in FIG. 1, and connected to each other in any convenient manner, not shown in the drawing.
  • a switch valve 14 is arranged in the connecting plate 11 which communicates at one end with a fluid inlet 15 and intermediate its ends with a fluid outlet 16.
  • a valve member 17 of the switch valve 14 is biased by means of a spring 19 in the pressure chamber 18 of the valve in closing direction in which a control edge 21 of the valve member is moved to a position preventing flow from the inlet 15 to the outlet 16 through the switch valve.
  • a first control passage 22 communicates at opposite ends with the inlet 15 and the pressure chamber 18.
  • a first throttle 23 is provided in this control passage and a second throttle 25 is arranged in the first control passage 22 upstream of the first throttle.
  • the second throttle 25 has a greater open cross section than the first throttle 23.
  • a first branch passage 220 branches off from the first control passage 22 downstream of the first throttle 23 and a second branch passage 22b branches off from the first control passage 22 between the first and the second throttle, which branch conduits end at the face 24 at which the connecting plate 11 abuts against the control valve 12.
  • the connecting plate 11 is further formed with a passage 27 leading from the outlet 16 to the aforementioned face 24.
  • the control valve 12 has a housing 28 with a longitudinal bore 29 formed therethrough, which is at longitudinally spaced portions thereof enlarged to form an inlet chamber 31, two consumer chambers 32 and 33, two return flow chambers 34 and 35 and two adjacent control chambers 36 and 37.
  • the inlet chamber 31 is connected by a passage 39, in which a check valve 38 is arranged, with the branch passage 22b.
  • the two return flow chambers 34 and 35 are connected to each other by a passage 41.
  • the chamber 34 is further connected by a passage 42 to the return flow passage 27 in the connecting plate 11.
  • a passage 43 connects the control chamber 36 with the branch passage 22a in the connecting plate 11.
  • a passage 44 leads from the control chamber 37 to the face of the housing 28 which abuts against the end plate 13.
  • a passage 56 formed in the end plate 13 connects the aforementioned passage 44 with a passage 42a leading from this end face into the return flow chamber 34.
  • a pair of conduits 58 and 59 respectively lead from the chambers 32 and 33 through the housing 28 and the end plate 13 to aconsumer device, not shown in the drawing.
  • a valve spool 45 is closely guided in the cylinder bore 29 and the spool is provided with a plurality of spaced piston sections, the outer surfaces of which engage the inner surface of. the bore,
  • the control edges 48 of the piston sections 46 and 47 are provided with cutouts or chamfers 49 which taper in the direction away from the respective control edge for controlling flow of fluid from the chambers 31 and 33 to the conduits 58 and 59.
  • Two additional piston sections 51 and 52 are provided with similar cutouts or chamfers 54 at their control edges 53 for controlling flow of fluid from the passage 43 into the passage 44.
  • a double acting return device 55 biases the spool 45 to the neutral position, as shown in FIG. 1, from which it is movable in opposite directions to a plurality of working positions.
  • valve spool 45 of the control valve 12 If the valve spool 45 of the control valve 12 is moved toward the right, as viewed in FIG. 1, the control edge 53 on the piston section 51 with its cutout or chamfer 54 will throttle flow of fluid through the control passage means 57. This will cause the pressure in the pressure chamber 18 to rise and therewith also the pressure at the inlet 15. When now the pressure at the inlet 15 surpasses the sum of the pressure of the consumer device and the resistance of the check valve 38, pressure fluid will flow from the inlet 15, through the second throttle 25, the passages 22a and 39, the inlet chamber 31, past the control edge 48 of the piston section 47, into the consumer chamber 33.
  • the pressure medium flowing back from the consumer device may pass from the other consumer chamber 32 into the return flow chamber 34 and from there through the passages 42 and 27 to the outlet 16. Due to the pressure medium stream which flows to the consumer device, an additional pressure difference will be created-at the second throttle 25.
  • the total pressure drop produced by the first and the second throttle 23 and 25 will be determined by the spring 19 and will remain constant for each position of the valve member 17. In other words, the pressure of the fluid medium at the inlet 15 will act at one end of the valve member 17, tending to move the valve member toward the right, as viewed in FIG. 1, whereas the force of the spring 19 and the fluid pressure reduced by the pressure drop at the first and the second throttle will act on the other end of the valve member 17, tending to move the latter toward the left.
  • FIG. 4 illustrates the mentioned increase of the pressure p at the inlet 15 in dependency on the displacement s of the spool 45 according to curve 61 and depending on different pressures of the consumer device according to the curves 6265.
  • the pressure increase at the transition from the line 62 to the lines 62-65 is thereby, due to the influence of the second throttle 25 relatively small, this influence will increase with increased displacement of the spool 45.
  • FIG. 2 illustrates the corresponding curves 66-69 for a control device according to the prior art which does not have a second throttle 25.
  • the pressure increase proceeds along the curve 61 at low pressure in the consumer device up to a multiple of the pressure in the consumer device before it drops down again according to the curves 66-69 to the predetermined consumer device pressures. At a high pressure in the consumer device, the pressure increase will lead to an opening of the pressure limiting valve as can be noticed from the flattening of the curve 69.
  • FIGS. 3 and 5 illustrate the change of the amount of fluid flow q in dependence on the deflection s of the spool 45 in a control arrangement according to the prior art, respectively in the control arrangement of the present invention at different pressures in the consumer device.
  • the spool 45 will evidently also cooperate with the other elements of the disclosed control arrangement to produce a very fine control of the fluid passing therethrough when the spool 45 is moved from its neutral position towards the left.
  • valve member 17 may to gether with the pressure limiting valve 26 form a precontrolled pressure limiting valve.
  • the control valve 12 may also be constructed in different manner as above described and be provided with a control member cooperating with a plurality of valve seats. In both constructions of the control valve it is immaterial whether the desired control function will be performed by a single control member or by two control members which are spaced from each other.
  • a hydraulic control arrangement comprising a fluid inlet and a fluid outlet; switch valve means communicating with said inlet and said outlet and having a valve member movable between an open position permitting flow of fluid from said inlet to said outlet through said switch valve means and a closed position preventing such flow, and spring means biasing said valve member to said closed position; first control passage means providing constant communication between said inlet and said switch valve means and connected in parallel to the latter so that fluid passing through said first control passage means acts on said valve member in the same direction as said spring means; second control passage means communicating at one end with said first control passage means; a first throttle in said first control passage means upstream of said one end of said second control passage means; a second throttle arranged in said first control passage means upstream of said first throttle and having an open crosssection which remains constant during operation; return flow passage means communicating at one end with said outlet and adapted to communicate at the other end with the other end of said second control passage means; inlet passage means communicating at one end with said first control passage means between said first and said second throttle therein; and control
  • control member in said neutral position permits free flow of fluid from said second control passage means to said return flow passage means and in each of said working positions throttles such flow.
  • control member of said control valve means is in the form of an elongated spool movable in axial direction between said positions thereof, said spool having sections provided with cutouts of gradually varying cross section for fine regulating flow of fluid passing through said second control passage means.

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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)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
US434343A 1973-01-24 1974-01-17 Hydraulic control arrangement Expired - Lifetime US3924655A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2303286A DE2303286C2 (de) 1973-01-24 1973-01-24 Hydraulische Steuereinrichtung

Publications (1)

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US3924655A true US3924655A (en) 1975-12-09

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ID=5869776

Family Applications (1)

Application Number Title Priority Date Filing Date
US434343A Expired - Lifetime US3924655A (en) 1973-01-24 1974-01-17 Hydraulic control arrangement

Country Status (6)

Country Link
US (1) US3924655A (enrdf_load_stackoverflow)
JP (1) JPS5925881B2 (enrdf_load_stackoverflow)
DE (1) DE2303286C2 (enrdf_load_stackoverflow)
FR (1) FR2214828B1 (enrdf_load_stackoverflow)
GB (1) GB1427466A (enrdf_load_stackoverflow)
IT (1) IT1003472B (enrdf_load_stackoverflow)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109561A (en) * 1976-11-26 1978-08-29 Caterpillar Tractor Co. Control valve arrangement with a preconditioned relief valve and a flow force compensated valve spool
US4176685A (en) * 1978-02-09 1979-12-04 Robert Bosch Gmbh Valve arrangement for controlling the flow of hydraulic fluid to and from a user
US4325410A (en) * 1978-01-31 1982-04-20 Wolfgang Bernhardt Control device for a hydraulically operated load
US4616675A (en) * 1984-02-23 1986-10-14 Mannesmann Rexroth Gmbh Solenoid-actuated directional control valve
US4693273A (en) * 1984-04-04 1987-09-15 Lucas Industries Public Limited Company Control valve
US20060144451A1 (en) * 2003-03-28 2006-07-06 Aisin Seiki Kabushiki Kaisha Hydraulic pressure control device
JP2007309459A (ja) * 2006-05-19 2007-11-29 Denso Corp 電磁弁

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2716694A1 (de) * 1977-04-15 1978-10-19 Bosch Gmbh Robert Steuereinrichtung fuer einen hydraulischen arbeitszylinder
DE3007787A1 (de) * 1980-02-29 1981-09-17 Linde Ag, 6200 Wiesbaden Steuereinrichtung mit einem schieberventil mit feinsteuernuten am steuerschieber
DE3141143A1 (de) * 1981-10-16 1983-04-28 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische steuereinrichtung
JPS6051301U (ja) * 1983-09-16 1985-04-11 株式会社トキメック 昇降装置の液圧回路
CN106051277A (zh) * 2016-07-11 2016-10-26 润琛液压机械南通有限公司 一种锚机专用液压阀

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3722543A (en) * 1971-11-02 1973-03-27 Hydraulic Industries Pressure compensated control valve

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2489435A (en) * 1948-03-22 1949-11-29 Vickers Inc Power transmission
DE1090480B (de) * 1957-07-19 1960-10-06 Kaemper Motoren G M B H Steuereinrichtung fuer vorzugsweise mehrere von einer Pumpe versorgte hydraulische Antriebe
DE1475958B2 (de) * 1965-11-20 1972-10-12 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung fuer mindestens zwei von einer druckmittelquelle gespeiste hydraulische verbraucher

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3722543A (en) * 1971-11-02 1973-03-27 Hydraulic Industries Pressure compensated control valve

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109561A (en) * 1976-11-26 1978-08-29 Caterpillar Tractor Co. Control valve arrangement with a preconditioned relief valve and a flow force compensated valve spool
US4325410A (en) * 1978-01-31 1982-04-20 Wolfgang Bernhardt Control device for a hydraulically operated load
US4176685A (en) * 1978-02-09 1979-12-04 Robert Bosch Gmbh Valve arrangement for controlling the flow of hydraulic fluid to and from a user
US4616675A (en) * 1984-02-23 1986-10-14 Mannesmann Rexroth Gmbh Solenoid-actuated directional control valve
US4693273A (en) * 1984-04-04 1987-09-15 Lucas Industries Public Limited Company Control valve
US20060144451A1 (en) * 2003-03-28 2006-07-06 Aisin Seiki Kabushiki Kaisha Hydraulic pressure control device
JP2007309459A (ja) * 2006-05-19 2007-11-29 Denso Corp 電磁弁

Also Published As

Publication number Publication date
JPS49104079A (enrdf_load_stackoverflow) 1974-10-02
IT1003472B (it) 1976-06-10
FR2214828A1 (enrdf_load_stackoverflow) 1974-08-19
DE2303286C2 (de) 1982-03-11
GB1427466A (en) 1976-03-10
FR2214828B1 (enrdf_load_stackoverflow) 1978-02-10
JPS5925881B2 (ja) 1984-06-22
DE2303286A1 (de) 1974-07-25

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