US2272684A - Hydraulically actuated member and speed control therefor - Google Patents

Hydraulically actuated member and speed control therefor Download PDF

Info

Publication number
US2272684A
US2272684A US26052639A US2272684A US 2272684 A US2272684 A US 2272684A US 26052639 A US26052639 A US 26052639A US 2272684 A US2272684 A US 2272684A
Authority
US
United States
Prior art keywords
pressure
valve
chamber
piston
liquid
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
Other languages
English (en)
Inventor
Harry F Vickers
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.)
Vickers Inc
Original Assignee
Vickers Inc
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
Priority to DEV28299D priority Critical patent/DE650404C/de
Application filed by Vickers Inc filed Critical Vickers Inc
Priority to US26052639 priority patent/US2272684A/en
Application granted granted Critical
Publication of US2272684A publication Critical patent/US2272684A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/22—Feeding members carrying tools or work
    • B23Q5/26—Fluid-pressure drives
    • B23Q5/266—Fluid-pressure drives with means to control the feed rate by controlling the fluid flow
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7787—Expansible chamber subject to differential pressures
    • Y10T137/7788—Pressures across fixed 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
    • Y10T137/7793—With opening bias [e.g., pressure regulator]

Definitions

  • This invention relates to a hydraulically actuated member and speed control therefor, and has to do particularly with liquid actuated devices which are subject to a variable speed or a. variable load.
  • variable pump in the control of the speed of liquid actuated devices, such as machine tools and the like, it has been the practice to make use of systems embodying either a variable displacement pump or a constant displacement pump.
  • variable pump In systems using variable pumps, it is the practice to set the pump corresponding to a certain load and predetermined speed. Theoretically, such variable pump should maintain a constant speed of the liquid actuated element regardless of a varying load, but practically, there is a change in slippage in such pumps which results in a slowing down when an increased load is met or an increase in speed equivalent to the amount of slippage when load is released.
  • variable pumps In practice, in systems using variable pumps, fairly good results are often obtained when the work is irst set up, but when the oil warms up and thins, and as the tools become dull, there is a noticeable slowing up due to a change in the slippage in the variable pump.
  • the object of the present invention to provide means operating independently of the particular type of pump used and independently of the viscosity of the liquid used, to uniformly and positively control the speed of any liquid actuated member; this control of speed being either uniform regardless of the load, or variable relative to any change in load. More specically, the present invention utilizes the principle that if a given pressure diiferential is maintained across a given size orifice the flow through said orifice will remain constant.
  • My complete system as contemplated in the present invention, embodies a liquid actuated member such as a machine tool element which is subjected to a variable load either positive or negative during its movement in any given direction, a source of uid supply under pressure, an obviously regulable to control the ow of liquid therethrough, and hence the speed of the liquid actuated element, and means operating in combination with the other elements of the system to positively control the pressure diierential across the perennial to maintain or control the predetermined speed.
  • a liquid actuated member such as a machine tool element which is subjected to a variable load either positive or negative during its movement in any given direction, a source of uid supply under pressure, an sunt regulable to control the ow of liquid therethrough, and hence the speed of the liquid actuated element, and means operating in combination with the other elements of the system to positively control the pressure diierential across the perennial to maintain or control the predetermined speed.
  • This means embodies a hydrostatic pressure regulating valve, preferably in combination as a single unit with a variable tone, said hydrostatically operating valve being so arranged and proportioned that any change in pressure due to a change in load can be made to increase, decrease or maintain the pressure in a certain part of the valve and hence cause the differential pressure across the orifice to either increase, decrease, or maintain constant the speed of the liquid actuated element, as desired.
  • Fig. 1 is a somewhat diagrammatic view of a complete liquid circulating system embodying the present invention, and showing particularly the manner of connecting my speed control valve into the system whereby to control the speed oi the liquid actuated element in one direction.
  • Fig. 2 is a sectional view of my hydrostatic 0I speed control valve as embodied in a single complete unit, the balanced valve being shown in raised seated position.
  • Fig. 3 is a front elevation of the complete unit and showing the adjustable indicating lever for regulating the size of the discharge orifice.
  • Fig. 4 is a fragmentary sectional view of the end of the balanced valve and showing a modified manner of varying the eifective diameter of one end of the valve.v
  • Fig. 5 is a somewhat diagrammatic assembly view of a circulating system embodying the present invention and showing the manner of connecting my speed control valve into the discharge side of the system, and controlling the speed of the liquid actuated member in opposite directions of movement.
  • Fig. 6 is a view similar to Fig.,5, but illustrating the manner of connecting the speed control unit into the intake side of the system.
  • said valve consists of a housing 2 which is provided with a chamber 3 in communication with the incoming liquid and a chamber 4 for connecting a balanced inlet valve 5 and a variable oriiice outlet valve 6.
  • This outlet valve 6 controls the volume of liquid passing into the outlet 1.
  • the balanced valve 5 is connected by means of a stem 8 to a piston 9, the diameter A1 of the stem at the point III being predetermined relative to the effective diameter AT of the valve 5 at its valve seat.
  • the diameter of the portion I0 of the valve stem will be equal to the effective diameter of the valve 5, but such respective diameters may be varied as will be later described.
  • di ameter A2 is shown smaller than diameter A1.
  • a coil spring II of predetermined pressure is so positioned as to normally tend to open the valve 5.
  • the chamber 4 is in direct communication with a'chamber I2 on one side of the piston 9 by means of a passageway I3 so that the strength of the spring II as balanced against the pressure upon the area. of the piston 9 determines the opening of the valve 5.
  • the space I4 on the other side of the piston 3 is in communication, by means of the passageway I5, with the outlet passageway 1 to compensate for any back pressure under any operating conditions, as, for instance, when a long pipe connected to the outlet 1 would set up a material amount of resistance.
  • the back pressure in the line 1 will vary and one of the varients will be the length of the pipe 1, but as the back pressure in the pipe I5 is effective against the top of piston 9 it will be seen that the combination of the spring II, piston 9, conduit' I3, valve 5, and tone 6 will maintain head in the chamber 4, or in other words, a constant dierential pressure across the orifice regardless of the amount of back pressure in pipe I5.
  • the housing 2 also preferably provides a suitable bearing for supporting a shaft I 6 rigidly connected to the variableiser valve 6 and actuated by means of a suitable lever I1. It will thus be evident that the orifice may be readily adjusted to any predetermined opening by moving the lever I1 to the desired point on the graduated scale at the face of the unit.
  • a simple circuit is shown as comprising a constant displacement type pump I8, a relief valve I9, a four-way control valve 20, a cylinder 2I containing a liquid actuated element or piston 22, a check valve 23, a feed control valve 2, and a tank 24; the liquid flows through the pump I8, relief valve I9 and four-way valve 2U, to one end of the cylinder 2
  • the pressure in the chamber 4 will be maintained constant, for any given spring, regardless of the opening of the orifice provided with a valve 6. Any tendency to increase the pressure in the line and in the chamber 3 will be immediately reflected in the chamber I2 to raise the piston and valve 5 towards valve closing position. Likewise, any pressure drop in the chamber 3 will be immediately reected in the chamber I2 and the spring II will immediately open or enlarge the opening past the valve 5 and admit more liquid to the chamber 4 to maintain pressure therein.
  • the pressure in the chamber 4 will vary in accordance with any variation in the ,back pressure, but the differential between the pressure in the chamber 4 and that in the line I will be maintained regardless of any change in back pressure.
  • the ow past such orifice will, of necessity, be constant for any given opening of the orifice 6; if the rate of ow is constant on the exhaust side of the motor, then regardless of the load upon the piston 22 of the motor and up to the capacity of the setting of the relief valve I9, the speed of the piston 22 will be maintained at the rate set above the orifice opening.
  • the relief valve IS is set to equal the maximum desired load on the piston 22.
  • the speed control unit 2 will, of course, have less capacity, when operating to control the speed of the piston 22, than the capacity of the pump I8.
  • the pump I8 has a iive gallon per minute capacity, and a certain setting of the speed control unit 2 a one-half gallon per minute capacity, and if the maximum load on the piston 22 and the maximum setting of the relief valve I9 should be say two thousand pounds, then if the pump is started up and the liquid directed into the inlet side of the cylinder 2
  • the diameter A1 of the stem .at the point I bear a certain predetermined relation to the effective diameter A2 of the valve 5.
  • these two diameters are preferably equal so that pressure in the chamber 3 will not impart either a downward er upward force on the piston 9.
  • the effective diameter of the valve l will preferably be made smaller than the effective diameter at the point lil (as shown in Fig. 2). In this case, any drop in pressurc in the line 25 due to a sudden load will cause an increase of the pressure in the chamber 4, thus maintaining increased speed during the effective period of said increase in load, as will hereinafter be explained in greater detail.
  • Fig. 5 I have shown my hydraulic system as applied to a member to be actuated in whichv the speed thereof is controlled in both directions.
  • the four-way valve 20 controls the ow of liquid under pressure alternately to opposite sides of the piston 22.
  • this piston 22 may control the actuation of a turret head, or any other machine tool element.
  • will be directed by the four-Way valve through the pipe 24 tothe speed control unit, and this four-way valve will control the application of the pressure to the vomsky 6, regardless of the pressure in the chamber 3, in the same manner as described in connection with the operation of the circuit shown in Fig. 1.
  • a rapid traverse valve 30 may be inserted as a shunt around the speed control unit 2 to bypass the speed control unit 2 when desired.
  • Fig. 5 approximate pressures that might exist in the valve system in a certain condition of operation.
  • the pump I8 could be regulated by setting the relief valve I9 to deliver seven hundred and fty pounds per square inch, which pressure will be directed by means of the valve to the left hand side of the piston 22.
  • the pressure on'the discharge side will be approximately 640 pounds per square inch and approximately this same pressure will be present in the chamber 3 of the unit 2.
  • variable valve 6 may be set to obtain any speed desired of the work element, regardless of a negative or positive load in a single direction of movement and in every such set-up the pressure in the chamber 4 will remain constant at ten pounds per square inch.
  • Fig. 6 I have shown a slightly modified hydraulic hook-up wherein the speed control unit 2 is placed in the intake side of the system.
  • This particular hydraulic hook-up may be utilized with many machine tools and other elements and has practically all the advantages of the of a sudden release of the load as in case wherein the drill has protruded through the work and g the inertia force of the weight of the drill head would be greater than the force exerted by the vacuum behind the piston.
  • the lever l1 may be placed in any position to give the required speed.
  • the pump I8 may then be started and the liquid under pressure flows through the four-way valve 20 into the upper end of the cylinder 2
  • the pressure in chamber 4 builds up due to restriction of the orifice member 5
  • the pressure on the lower side of the piston 9 overcomes the spring Il closing the valve 5 to the point where flow through this valve just supplies sufiicient volume to maintain a predetermined pressure in the chamber 4.
  • a sleeve 26 or a valve 5a is selected with a diameter smaller than the diameter of the stem I0.
  • any drop in the pressure in chamber I will reduce the reaction against the spring Il and result in a proportionate increase in pressure in 4; in other words, with the control valve balanced the presany unequalness in the sure in 4 will always remain constant regardless of conditions in the system, b ut with the valve unbalanced the pressure in 4 will be proportional to the unbalancing pressure.
  • areas 5 and l0 will add to or subtract from the effective spring load on the piston and will effect a proportional change in the pressure in chamber 4.
  • An increase or decrease of the pressure in chamber 4- increases or decreases the flow through the valve 8. It will therefore be obvious that with areas 5 andv Il unbalanced a change in pressure in chamber I causes a proportional change in chamber 4 which is either in direct or inverse relation to -the change in 3 depending upon whether the effective area of 5 is larger or smaller than Il.
  • the main use for this feature is4 duel to the fact that all hydraulic motors have some slip or leakage and an increase in load causes an increase in slip due to the increased pressure differential across the piston and it is therefore possible to select a speed control valve 5 so that a change in load will cause no change in piston speed.
  • a liquid controlling system comprising in combination a liquid operated motor, a source of liquid under pressure and aspeed control device all operatively connected, said device including a control valve having opposed pressure surfaces and a regulable orifice member, said member and valve being operatively connected through a pressure chamber, the pressure in said chamber controlling the flow through the orifice member to control the speed of the motor, said opposed pressure surfaces being unbalanced to maintain a pressure in the pressure chamber in proportion to the unbalancing of said pressure surfaces whereby to increase or decrease the speed of the motor upon a variation in load.
  • a hydraulic motor operatively connected with the motor, a speed control unit therefor embodying a chamber for receiving the liquid supply, a variable discharge orifice member, a chamber on the intake side of said orifice member, a valve between said two chambers having opposed pressure surfaces, elements forming the effective size of one of said pressure surfaces, one of said elements being replaceable to vary the size of said one surface, and a spring pressed piston operatively connected with said valve for controlling the pressure in said second named chamber to control the pressure differential across the orifice member.
  • a hydraulic motor including a chamber for receiving the normal liquid flow from the motor, a secondchamber leading to a discharge orifice member of predetermined size, a piston valve having opposed pressure surfaces for controlling the flow between said two chambers, a piston connected to said valve, a conduit for connecting the second chamber with one side of the piston, one of said opposed pressure surfaces being of different relative effective diameter to vary the pressure in the second chamber in proportion with a change in load in the motor.
  • a hydraulic motor having a piston and cylinder, a hydraulic circuit including a pump directly connected with said motor, a relief valve in said'circuit for determining the maximum. preloading of one side of said piston, a directional valve for the motor, and a speed control unit comprising a regulable orifice valve, a pressure chamber on one side of said orifice valve and a discharge conduit leading from the unit on the other side, a spring pressed piston having one face exposed to the pressure in said chamber and the other face exposed to the pressure in said discharge conduit, a second chamber for receiving liquid from the motor, the flow of which is to be controlled, and ar piston valve formed as a part of said piston and extending into said second chamber, said piston valve having opposed pressure surfaces with different effective areas exposed to the pressure in said second chamber, the relative size of said different effective areas being predetermined to insure a predetermined relationship between the pressure in the first chamber and any change in pressure in the second chamber, and a passageway between said two chambers forming a valve seat for one of said pressure surfaces
  • a hydraulic motor having a piston and cylinder, a hydraulic circuit including a. pump directly connect-ed with said motor, a directional valve for the motor, and a speed control unit comprising a regulable orifice valve, a pressure chamber on one side of said perennial valve and a discharge conduit leading from the unit on the other side, a spring pressed piston having one face exposed to the pressure in said chamber and the other face exposed to the pressure in said discharge conduit, a second chamber for receiving liquid from the motor, the flow of which is to be controlled, and a piston valve formed as a part of said piston and extending into said second chamber, said piston valve having opposed pressure surfaces with different effective areas exposed to the pressure in said second chamber, the relative size of said different effective areas being predetermined to insure a predetermined relationship between the pressure in the first chamber and any change in pressure in the second chamber, and a passageway between said two chambers forming a valve seat for one of said pressure surfaces, said spring tending to separate said pressure surface and valve seat.
  • a hydraulic motor a hy ⁇ draulic circuit including a pump directly connected with said motor, a directional valve for the motor, and a speed control unit comprising a regulable orifice valve, a pressure chamber on one side of said orifice valve and a discharge conduit leading from the unit on the other side, a spring pressed piston having one face exposed to the pressure in said chamber and the other face exposed to the pressure in said discharge conduit, a second chamber for vreceiving liquid from the motor, the ow of which is to be controlled, and a piston valve formed as a part of said piston and extending into said second chamber, said piston valve having opposed pressure surfaces with different effective areas, than the area of the faces of said piston, exposed to the pressure in said second chamber, the relative size of said different effective areas being predetermined to insure a predetermined relationship between the pressure in the rst chamber and any change in pressure in the second chamber, and a passageway between said two chambers forming a valve seat for one of said pressure surfaces, said spring tending
  • a liquid controlling system comprising in combination a liquid operated motor, a source of liquid under pressure constantly preloading one side of said motor during a power stroke, and a speed control device all operatively connected, said device including a control valve having opposed pressure surfaces of different effective areas and a regulable orifice member, said member and valve being operatively connected through a pressure chamber, a spring pressed piston attached to said valve and subject to the pressure in said chamber, the pressure in said chamber controlling the flow through the orifice member to control the speed of the motor, the effective area of one of said pressure surfaces l being predetermined and so arranged relative to the effective area of the other pressure surface that any change in pressure in liquid leading from the motor due to change in load on the motor will predetermine the pressure in said chamber in accordance with said relative effective diameters.
  • a flow control unit for use with a hydraulic motor circuit of the type having a piston and cylinder motor unit, and pump for applying positive pressure to one side of the piston during its entire working stroke, comprising a regulable orifice valve, a pressure chamber on one side of said valve and a discharge conduit leading from the other side, a spring pressed piston having one face exposed to the pressure in said chamber and the other face exposed to the pressure in said discharge conduit, a second chamber for receiving liquid from the other side of said motor piston, and a piston valve formed as an extension of said piston and extending into said second chamber, said piston valve having opposed pressure surfaces of appreciably smaller size than the effective area of said piston, said pressure surfaces being so proportioned relative toy each other as to predetermine the effect of the pressure in said second chamber upon the pressure in said first chamber, and elements cooperating to form the effective area of one of said surfaces, one of said elements being replaceable to change the relation between the effective areas of said opposed surfaces.
  • a ow control'unit for use with a hydraulic motor circuit of the type having a piston and cylinder motor unit, and pump for applyingV positive pressure to one side of the piston during its entire Working stroke, comprising a regulable orifice valve, a pressure chamber on one side of said valve and a discharge conduit leading from the other side, a spring pressed piston having one face exposed to the pressure in said chamber and the other face exposed to the pressure in said discharge conduit, a.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
US26052639 1931-06-12 1939-03-08 Hydraulically actuated member and speed control therefor Expired - Lifetime US2272684A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DEV28299D DE650404C (de) 1931-06-12 1932-06-14 Vorrichtung zur Steuerung der Bewegung eines durch Fluessigkeit beeinflussten Teiles
US26052639 US2272684A (en) 1931-06-12 1939-03-08 Hydraulically actuated member and speed control therefor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US54390831A 1931-06-12 1931-06-12
US26052639 US2272684A (en) 1931-06-12 1939-03-08 Hydraulically actuated member and speed control therefor

Publications (1)

Publication Number Publication Date
US2272684A true US2272684A (en) 1942-02-10

Family

ID=26948053

Family Applications (1)

Application Number Title Priority Date Filing Date
US26052639 Expired - Lifetime US2272684A (en) 1931-06-12 1939-03-08 Hydraulically actuated member and speed control therefor

Country Status (2)

Country Link
US (1) US2272684A (de)
DE (1) DE650404C (de)

Cited By (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421219A (en) * 1942-03-04 1947-05-27 Landis Tool Co Balancing valve
US2462796A (en) * 1944-12-11 1949-02-22 Bendix Aviat Corp Regulator
US2487520A (en) * 1944-12-26 1949-11-08 Vickers Inc Hydraulic power transmission with bypass flow control valve
US2495785A (en) * 1945-01-11 1950-01-31 Hydraulic Equipment Company Lowering valve
US2501483A (en) * 1948-04-03 1950-03-21 Warner Swasey Co Hydraulic power system
US2526835A (en) * 1946-10-18 1950-10-24 Hpm Dev Corp Hydraulic motor control
US2536558A (en) * 1946-01-04 1951-01-02 Keelavite Co Ltd Pump and motor hydraulic transmission system
US2546579A (en) * 1946-08-13 1951-03-27 Denison Eng Co Fluid motor control mechanism
US2587449A (en) * 1945-02-10 1952-02-26 Farmingdale Corp Hydraulic feed for machine tools
US2603235A (en) * 1952-07-15 Kirkham
US2618932A (en) * 1949-09-09 1952-11-25 Vickers Inc Pump and motor hydraulic system, including multiple pumps
US2620679A (en) * 1949-04-13 1952-12-09 Morris Motors Ltd Power transmission for motor vehicles
US2655902A (en) * 1949-12-22 1953-10-20 Askania Regulator Co System for proportioning fluid flow to control signal magnitude
US2657906A (en) * 1947-09-18 1953-11-03 Buda Co Earth drill
US2752895A (en) * 1951-03-09 1956-07-03 Bendix Aviat Corp Hydraulic motor and control therefor
US2825358A (en) * 1954-03-01 1958-03-04 Oilgear Co Pressure regulator
US2833374A (en) * 1954-07-07 1958-05-06 Sidney P Glasser Constant flow lube system
US2855752A (en) * 1955-10-21 1958-10-14 Brusque Rene Le Hydraulic device for controlling the feed and stop position of a machine element in cutting, sawing and slicing machines
US2862523A (en) * 1955-04-18 1958-12-02 Dole Valve Co Thermostatic fluid restrictor
US2903007A (en) * 1950-04-28 1959-09-08 Gpe Controls Inc Compensation of back pressure variation in discharge type regulators
US2951501A (en) * 1954-09-20 1960-09-06 Separator Ab Regulating device for a flow medium
US2953152A (en) * 1956-08-17 1960-09-20 Thompson Ramo Wooldridge Inc Pressure regulating valve
US2982258A (en) * 1957-06-04 1961-05-02 United Aircraft Corp Pressure ratio device utilizing a free piston valve for pressure ratio regulation and a servo mechanism coacting therewith to amplify pressure ratio error correction
US3015350A (en) * 1957-10-14 1962-01-02 Swift & Co Bacon slicer having adjustable control of group size
US3046950A (en) * 1958-01-22 1962-07-31 Whiting Corp Constant mechanical advantage rotary hydraulic device
US3088688A (en) * 1958-09-25 1963-05-07 H G Weber And Company Inc Hydraulic system
US3115892A (en) * 1954-10-11 1963-12-31 Fischer & Porter Co Flow controller
US3119306A (en) * 1960-08-01 1964-01-28 Onsrud Machine Works Inc Contouring and profiling machines
US3132485A (en) * 1961-03-31 1964-05-12 Blackhawk Mfg Co Hydraulic motor control
US3212525A (en) * 1962-10-18 1965-10-19 Henderson Hallie Valves for refrigeration apparatus having cooling and/or heating cycles
US3437012A (en) * 1965-12-28 1969-04-08 Asea Ab Valve system for hydraulic elevators
US3596677A (en) * 1969-01-13 1971-08-03 Rex Chainbelt Inc Remotely operable pressure compensated flow control valve
US3678952A (en) * 1968-10-22 1972-07-25 Honda Motor Co Ltd Pressure fluid circuit in automatic transmission apparatus
US3795260A (en) * 1972-09-27 1974-03-05 G Bergson Three way valve for flow regulator connected to moisture analyzer
US4147179A (en) * 1976-02-24 1979-04-03 Shoketsu Kinzoku Kogyo Co., Ltd. Pressure governor valve equipped with flow control valve
US4175473A (en) * 1976-06-08 1979-11-27 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Fluid circuit
DE2826613A1 (de) * 1978-06-19 1979-12-20 Werner & Pfleiderer Stromregelventil
US4271864A (en) * 1980-03-31 1981-06-09 Mac Valves, Inc. Pressure regulating valve
US4420014A (en) * 1980-04-21 1983-12-13 The Bendix Corporation Pressure regulator for a fluid motor
US4779419A (en) * 1985-11-12 1988-10-25 Caterpillar Inc. Adjustable flow limiting pressure compensated flow control
US4811649A (en) * 1987-02-18 1989-03-14 Heilmeier & Weinlein, Fabrik Fur Oelhydraulik Gmbh & Co. Kg Hydraulic control apparatus
US5107886A (en) * 1991-02-15 1992-04-28 Taylor Julian S Constant flow orifice valve
US5282490A (en) * 1989-12-18 1994-02-01 Higgs Robert E Flow metering injection controller
US5460199A (en) * 1992-07-13 1995-10-24 Sumitomo Electric Industries, Ltd. Flow control valve and control method therefor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1151713B (de) * 1954-09-11 1963-07-18 Klopp Werke G M B H Steuervorrichtung fuer Hobelmaschinen, insbesondere Schnellhobler

Cited By (46)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2603235A (en) * 1952-07-15 Kirkham
US2421219A (en) * 1942-03-04 1947-05-27 Landis Tool Co Balancing valve
US2462796A (en) * 1944-12-11 1949-02-22 Bendix Aviat Corp Regulator
US2487520A (en) * 1944-12-26 1949-11-08 Vickers Inc Hydraulic power transmission with bypass flow control valve
US2495785A (en) * 1945-01-11 1950-01-31 Hydraulic Equipment Company Lowering valve
US2587449A (en) * 1945-02-10 1952-02-26 Farmingdale Corp Hydraulic feed for machine tools
US2536558A (en) * 1946-01-04 1951-01-02 Keelavite Co Ltd Pump and motor hydraulic transmission system
US2546579A (en) * 1946-08-13 1951-03-27 Denison Eng Co Fluid motor control mechanism
US2526835A (en) * 1946-10-18 1950-10-24 Hpm Dev Corp Hydraulic motor control
US2657906A (en) * 1947-09-18 1953-11-03 Buda Co Earth drill
US2501483A (en) * 1948-04-03 1950-03-21 Warner Swasey Co Hydraulic power system
US2620679A (en) * 1949-04-13 1952-12-09 Morris Motors Ltd Power transmission for motor vehicles
US2618932A (en) * 1949-09-09 1952-11-25 Vickers Inc Pump and motor hydraulic system, including multiple pumps
US2655902A (en) * 1949-12-22 1953-10-20 Askania Regulator Co System for proportioning fluid flow to control signal magnitude
US2903007A (en) * 1950-04-28 1959-09-08 Gpe Controls Inc Compensation of back pressure variation in discharge type regulators
US2752895A (en) * 1951-03-09 1956-07-03 Bendix Aviat Corp Hydraulic motor and control therefor
US2825358A (en) * 1954-03-01 1958-03-04 Oilgear Co Pressure regulator
US2833374A (en) * 1954-07-07 1958-05-06 Sidney P Glasser Constant flow lube system
US2951501A (en) * 1954-09-20 1960-09-06 Separator Ab Regulating device for a flow medium
US3115892A (en) * 1954-10-11 1963-12-31 Fischer & Porter Co Flow controller
US2862523A (en) * 1955-04-18 1958-12-02 Dole Valve Co Thermostatic fluid restrictor
US2855752A (en) * 1955-10-21 1958-10-14 Brusque Rene Le Hydraulic device for controlling the feed and stop position of a machine element in cutting, sawing and slicing machines
US2953152A (en) * 1956-08-17 1960-09-20 Thompson Ramo Wooldridge Inc Pressure regulating valve
US2982258A (en) * 1957-06-04 1961-05-02 United Aircraft Corp Pressure ratio device utilizing a free piston valve for pressure ratio regulation and a servo mechanism coacting therewith to amplify pressure ratio error correction
US3015350A (en) * 1957-10-14 1962-01-02 Swift & Co Bacon slicer having adjustable control of group size
US3046950A (en) * 1958-01-22 1962-07-31 Whiting Corp Constant mechanical advantage rotary hydraulic device
US3088688A (en) * 1958-09-25 1963-05-07 H G Weber And Company Inc Hydraulic system
US3119306A (en) * 1960-08-01 1964-01-28 Onsrud Machine Works Inc Contouring and profiling machines
US3132485A (en) * 1961-03-31 1964-05-12 Blackhawk Mfg Co Hydraulic motor control
US3212525A (en) * 1962-10-18 1965-10-19 Henderson Hallie Valves for refrigeration apparatus having cooling and/or heating cycles
US3437012A (en) * 1965-12-28 1969-04-08 Asea Ab Valve system for hydraulic elevators
US3678952A (en) * 1968-10-22 1972-07-25 Honda Motor Co Ltd Pressure fluid circuit in automatic transmission apparatus
US3596677A (en) * 1969-01-13 1971-08-03 Rex Chainbelt Inc Remotely operable pressure compensated flow control valve
US3795260A (en) * 1972-09-27 1974-03-05 G Bergson Three way valve for flow regulator connected to moisture analyzer
US4147179A (en) * 1976-02-24 1979-04-03 Shoketsu Kinzoku Kogyo Co., Ltd. Pressure governor valve equipped with flow control valve
US4175473A (en) * 1976-06-08 1979-11-27 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Fluid circuit
DE2826613A1 (de) * 1978-06-19 1979-12-20 Werner & Pfleiderer Stromregelventil
US4271864A (en) * 1980-03-31 1981-06-09 Mac Valves, Inc. Pressure regulating valve
US4420014A (en) * 1980-04-21 1983-12-13 The Bendix Corporation Pressure regulator for a fluid motor
US4779419A (en) * 1985-11-12 1988-10-25 Caterpillar Inc. Adjustable flow limiting pressure compensated flow control
US4811649A (en) * 1987-02-18 1989-03-14 Heilmeier & Weinlein, Fabrik Fur Oelhydraulik Gmbh & Co. Kg Hydraulic control apparatus
US5282490A (en) * 1989-12-18 1994-02-01 Higgs Robert E Flow metering injection controller
US5427149A (en) * 1989-12-18 1995-06-27 Higgs; Robert E. Flow metering injection controller
US5107886A (en) * 1991-02-15 1992-04-28 Taylor Julian S Constant flow orifice valve
US5460199A (en) * 1992-07-13 1995-10-24 Sumitomo Electric Industries, Ltd. Flow control valve and control method therefor
US5524659A (en) * 1992-07-13 1996-06-11 Sumitomo Electric Industries, Ltd. Flow control valve and control method therefor

Also Published As

Publication number Publication date
DE650404C (de) 1937-09-22

Similar Documents

Publication Publication Date Title
US2272684A (en) Hydraulically actuated member and speed control therefor
US2285069A (en) Hydraulic feed control system
US2102865A (en) Combined flow control and relief valve
US1964196A (en) Regulator for hydraulic cylinders
US2043453A (en) Liquid relief valve
US2238063A (en) Fluid pressure system and valve mechanism therefor
US2328979A (en) Power transmission
US3018041A (en) Hydraulic function generator
US2238060A (en) Fluid pressure feed and rapid traverse system of transmission of power
US2139050A (en) Viscosity compensating device
US3402735A (en) Flow regulating apparatus
CA1096270A (en) Hydraulic control system
US3532104A (en) Pressure compensated flow control valve system
US2888943A (en) Control valve having constant volume output features
US2391930A (en) Power transmission system
US2111964A (en) Liquid flow control system
US2395633A (en) Fluid drive control valve
US1103036A (en) Controlling mechanism for hydraulic presses and the like.
US2415603A (en) Hydraulic constant speed control system for parallel-connected hydraulic motors
US2789576A (en) Hydraulic valve for constant speed control
US2296979A (en) Automatic variable speed control apparatus
US2803111A (en) Hydraulic servo systems
US2608986A (en) Fluid flow control valve
US2397395A (en) Hydraulic transmission
US2437113A (en) Fluid regulating device