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US3391708A - Valve - Google Patents

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Publication number
US3391708A
US3391708A US529473A US52947366A US3391708A US 3391708 A US3391708 A US 3391708A US 529473 A US529473 A US 529473A US 52947366 A US52947366 A US 52947366A US 3391708 A US3391708 A US 3391708A
Authority
US
United States
Prior art keywords
valve
passages
motor
check valve
passage
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
US529473A
Other languages
English (en)
Inventor
Orval L Rice
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.)
SPX Technologies Inc
Original Assignee
General Signal Corp
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 General Signal Corp filed Critical General Signal Corp
Priority to US529473A priority Critical patent/US3391708A/en
Priority to GB53395/66A priority patent/GB1120698A/en
Priority to DE19661550432 priority patent/DE1550432B2/de
Priority to FR94257A priority patent/FR1510663A/fr
Priority to SE2442/67A priority patent/SE308844B/xx
Application granted granted Critical
Publication of US3391708A publication Critical patent/US3391708A/en
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
    • 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
    • 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
    • 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
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • Valves of this kind are used frequently in hydraulic circuits for actuating double-acting motors.
  • Each general ly includes an inlet passage which is connected with a pump, an exhaust passage which is connected with a reservoir, first and second motor passages which are connected with opposite sides of the double-acting motor or cylinder, and a movable valve element.
  • the movable element has a neutral or hold position in which each motor passage is isolated from the other three passages, a raise position in which the first motor passage is connected with the inlet passage and the second motor passage is connected with the exhaust passage, and a lower position in which the connections between the motor passages and the inlet and exhaust passages are reversed.
  • the movable valve element or at least that portion of it controlling flow to and from the first motor passage, is of the hollow type, i.e., it contains an internal flow passage that forms part of the supply path to the motor in the raise position and part of the exhaust path from the motor in the lower position.
  • This internal flow passage is provided with a spring biased check valve which, in the raise position, prevents dropping of the load acting on the motor whenever pump supply pressure is below the pressure in the side of the motor that is being contracted by the load.
  • the object of this invention is to provide an improved regeneration scheme which, like the prior schemes mentioned above, uses the backpressure created by the load drop check valve to force fluid through the regeneration path, but which includes means for automatically changing the magnitude of the closing bias on the check valve in accordance with the position of the movable valve element.
  • the closing bias is set to the normal low value so that the supply flow to the cylinder is not unduly restricted.
  • this bias is increased to a higher value which will insure that the backpressure created by the load drop check. valve is adequate to maintain the expanding side 3,391,798 Patented July 9, 1968 of the cylinder liquid-filled. Since this invention allows the closing bias on the check valve to be matched to the requirements of the particular function which that valve is performing, it is obvious that it represents a more efiicient way of satisfying the needs of the hydraulic circuits in which the directional control valve is used.
  • FIG. 1 is a sectional view of one unit of a multi-plunger directional control valve of the tandem type incorporating the invention, the valve plunger being shown in the neutral position.
  • FIG. 2 and 3 are sectional views similar to FIG. 1 but showing the valve plunger in the raise and lower positions, respectively.
  • the invention is incorporated in one valve plunger 11 of a multi-plunger directional control valve of the series-parallel or tandem type.
  • the plunger 11 reciprocates in a valve bore 12 which extends through the housing of the valve, and which is encircled by seven longitudinally spaced, annular chambers 13-19; the chambers 15-17 forming part of the open center by-pass path of the directional control valve, the chambers 13 and 19 being connected by an exhaust manifold (not shown) with tank 21, and the chambers 14 and 18 being connected with the opposite sides of a doubleacting cylinder 22.
  • Valve plunger 11 is formed with a pair of annular peripheral grooves 23 and 24 which cooperate with chambers 15, 16 and 17 to complete the open center by-pass path, and which define three valve lands 2527. In the illustrated neutral position, lands 25 and 27 serve to isolate motor chambers 14 and 18 from each other and from the other chambers.
  • valve plunger 11 Extending into the right end of valve plunger 11 is a stepped axial bore whose open end is closed and sealed by a plug 28, and which is divided into two separate portions 29 and 31 by a sealed plug 32.
  • Bore portion 29 is intersected by two spaced sets of radial passages 33 and 34 which open through the outer surface of land 27 and are positioned to register, respectively, with chambers 17 and 18 in the lower position and with chambers 18 and 19 in the raise position.
  • a conventional load drop check valve 35 which seats on a step in bore portion 29, controls interpassage flow through bore portion 29.
  • Bore portion 31 cooperates with a pair of spaced sets of radial passages 35 and 37 to define a regenerative flow path which is controlled by by-pass valve 38.
  • the bypass valve 38 is adapted to seat on a step in bore portion 31 and is urged toward that seat by a coil compression spring 39 and by the fluid pressure in space 41 which communicates with radial passages 37 through radial and axial passages formed in the valve.
  • the by-pass valve 38 is shifted in the opening direction by the pressure in radial passages 36 which acts upon its nose 42.
  • valve plunger 11 Extending into the left end of valve plunger 11 is a second, stepped axial bore 43 whose open end is closed and sealed by plug 44 and which is intersected by three spaced sets of radial passages 45-47.
  • Passages 45 and 46 are positioned to register, respectively, with chambers 15 and 14- in the raise position, and passages 45 and 47 are positioned to register with chambers 14 and 13, respectively, in the lower position. In the lower position, radial passages 46 are closed by the wall of the bore 12.
  • valve 48 is a load drop check valve which is adapted to seat on a step in bore a 43 located between passages 45 and as, and the valve 49 serving to control the bias on the check valve 48 and being arranged to seat on a step located between passages 46 and 47.
  • Check valve 48 is biased closed by a light, coil compression spring 51 and by the fluid pressure in radial passages 46. These passages communicate with the space 52 behind the check valve through the radial clearance between the outer periphery of the stem of the check valve 43 and the wall of the axial recess in control valve 49 in which this stem is received.
  • the check valve is urged in the opening direction by the pressure in radial passages 45 which acts upon its nose 53.
  • Control valve 45 on the other hand, is biased closed by coil compression spring 54 and by the fluid pressure in radial passages 47, and is urged in the opening direction by the pressure in radial passages 46 which acts upon its annular nose 55.
  • Longitudinally extending grooves formed in the outer periphery of valve 49 connect radial passages 47 with the space 56 behind the valve.
  • Spring 54 exerts a greater biasing force than spring 51, and therefore, it maintains valve 49 on its seat against the unseating action of spring 51 which reacts against it.
  • chambers and 17 are connected with a supply pump 57, and chamber 16 is connected with tank 21. Either connection may be made directly through a housing port and a conduit, or indirectly through a path that includes the open center by-pass path provided by another valving unit.
  • valve plunger 11 With the valve plunger 11 in the illustrated neutral position, flow to and from chambers 14 and 13 is blocked by lands and 27, and the oil delivered by pump 57 passes to tank 21 via chambers 15 and 17, plunger grooves 23 and 24, and chamber 16. Therefore, cylinder 22 is hydraulically locked, and pump 57 is unloaded.
  • lands 25 and 26 interrupt flow from chambers 15 and 17 to chamber 16, and thus close the open center by-pass, and radial passages 33, 34, and 46 register with chambers 18, 19, 15 and 14, respectively.
  • the pump 57 now communicates with the rod end of cylinder 22 along a supply path including chamber 15, radial passages 45, check valve 48, radial passages 46, and motor chamber 14, and the head end of cylinder 22 is vented to tank 21 along an exhaust path including chamber 18, radial passages 33, bore portion 29, check valve 35, radial passages 34, and chamber 19. Opening of these flow paths causes cylinder 22 to move the load upward.
  • check valve 48 is opened initially, and then maintained open, by a pressure differential between passages 45 and 46 whose magnitude is a function of the small biasing force exerted by spring 51. Therefore, the pressure losses in the supply path to the rod end of cylinder 22 are no greater than those encountered in a conventional hollow plunger valve equipped with a load drop check valve.
  • Cylinder 22 moves the load downward when valve plunger 11 is shifted to the lower position shown in FIG. 3. In this position, lands 26 and 27 close the open center by-pass path, fluid from pump 57 is delivered to the head end of cylinder 22 along a path comprising chamber 17, radial passages 33, bore portion 29, check valve 35, radial passages 34 and chamber 13, and the return flow from the rod end of the cylinder is delivered to the axial bore 43 and bore portion 31 through chamber 14 and radial passages 45 and 36, respectively.
  • a directional control valve including a housing containing (a) inlet and exhaust passages and first and second motor passages;
  • a movable valving element having a first position in which it connects the first and second motor passages with the inlet and. exhaust passages, respectively, and a second position in which the connections between the motor passages and the other two passages are reversed, the valving element containing a load drop check valve which prevents flow from the first motor passage to the inlet passage in said first posilion and restricts flow from the first motor passage to the exhaust passage in the second position;
  • (d) means for exerting a closing bias on the load drop check valve which changes in accordance with the position of. the movable valving element, the larger bias being exerted when that element is in said second position.
  • bias exerting means comprises (a) a bias chamber in the valving element which is defined in part by the check valve itself so that the volume of the chamber decreases and increases as the check valve moves in the opening and closing directions, respectively;
  • control valve normally closing the second control passage but adapted to open this passage in response to a predetermined pressure in the bias chamber.
  • a movable valving element for a directional control valve including a body containing (a) a bore having closed ends and intersected intermedi ate these ends by three longitudinaily spaced transverse passages which open through the surface of the body, there being first and second end passages and an intermediate third passage;
  • first and second annular valve seats encircling the bore at points between the first and third passages and between the second and third passages, respectively;
  • a movable valving element as defined in claim 3 in which (a) the body is in the form of a sliding valve plunger;
  • the bore is an axial bore in the plunger
  • a movable valving element are defined in claim 4 in which (a) the control valve is guided for movement by the wall of said bore and contains an axial recess;
  • the check valve has a longitudinally extending stern which is received in said recess;

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
US529473A 1966-02-23 1966-02-23 Valve Expired - Lifetime US3391708A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US529473A US3391708A (en) 1966-02-23 1966-02-23 Valve
GB53395/66A GB1120698A (en) 1966-02-23 1966-11-29 Valve
DE19661550432 DE1550432B2 (de) 1966-02-23 1966-12-30 Richtungssteuerschieber
FR94257A FR1510663A (fr) 1966-02-23 1967-02-09 Distributeur hydraulique
SE2442/67A SE308844B (xx) 1966-02-23 1967-02-22

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US529473A US3391708A (en) 1966-02-23 1966-02-23 Valve

Publications (1)

Publication Number Publication Date
US3391708A true US3391708A (en) 1968-07-09

Family

ID=24110060

Family Applications (1)

Application Number Title Priority Date Filing Date
US529473A Expired - Lifetime US3391708A (en) 1966-02-23 1966-02-23 Valve

Country Status (5)

Country Link
US (1) US3391708A (xx)
DE (1) DE1550432B2 (xx)
FR (1) FR1510663A (xx)
GB (1) GB1120698A (xx)
SE (1) SE308844B (xx)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3459219A (en) * 1967-10-20 1969-08-05 Gen Signal Corp Regenerative valve plunger
US3642027A (en) * 1970-01-09 1972-02-15 Parker Hannifin Corp Directional control valve
US4020748A (en) * 1974-09-03 1977-05-03 Zahnradfabrik Friedrichshafen Ag Valve structure for hydraulic control system
US4518004A (en) * 1983-11-21 1985-05-21 Hr Textron Inc. Multifunction valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4840111A (en) * 1986-01-31 1989-06-20 Moog Inc. Energy-conserving regenerative-flow valves for hydraulic servomotors

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3200841A (en) * 1963-06-20 1965-08-17 New York Air Brake Co Valve
US3213880A (en) * 1963-06-19 1965-10-26 Int Harvester Co Hydraulic control valve
US3216446A (en) * 1963-02-05 1965-11-09 Parker Hannifin Corp Spool valve assembly with dual check valve assembly

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3216446A (en) * 1963-02-05 1965-11-09 Parker Hannifin Corp Spool valve assembly with dual check valve assembly
US3213880A (en) * 1963-06-19 1965-10-26 Int Harvester Co Hydraulic control valve
US3200841A (en) * 1963-06-20 1965-08-17 New York Air Brake Co Valve

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3459219A (en) * 1967-10-20 1969-08-05 Gen Signal Corp Regenerative valve plunger
US3642027A (en) * 1970-01-09 1972-02-15 Parker Hannifin Corp Directional control valve
US4020748A (en) * 1974-09-03 1977-05-03 Zahnradfabrik Friedrichshafen Ag Valve structure for hydraulic control system
US4518004A (en) * 1983-11-21 1985-05-21 Hr Textron Inc. Multifunction valve

Also Published As

Publication number Publication date
FR1510663A (fr) 1968-01-19
SE308844B (xx) 1969-02-24
DE1550432B2 (de) 1970-07-02
DE1550432A1 (de) 1969-04-10
GB1120698A (en) 1968-07-24

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