US1982711A - Combined rapid traverse and slow traverse hydraulic system - Google Patents

Combined rapid traverse and slow traverse hydraulic system Download PDF

Info

Publication number
US1982711A
US1982711A US569612A US56961231A US1982711A US 1982711 A US1982711 A US 1982711A US 569612 A US569612 A US 569612A US 56961231 A US56961231 A US 56961231A US 1982711 A US1982711 A US 1982711A
Authority
US
United States
Prior art keywords
pressure
liquid
pump
traverse
pumps
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
US569612A
Inventor
Harry F Vickers
Original Assignee
Harry F Vickers
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 Harry F Vickers filed Critical Harry F Vickers
Priority to US569612A priority Critical patent/US1982711A/en
Application granted granted Critical
Publication of US1982711A publication Critical patent/US1982711A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23QDETAILS, 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
    • B23Q5/00Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/02Driving main working members
    • B23Q5/027Driving main working members reciprocating members
    • B23Q5/033Driving main working members reciprocating members driven essentially by fluid pressure
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B15/00Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16Control arrangements for fluid-driven presses
    • B30B15/161Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure

Description

H. F. VICKERS Dec; 4, 1934.

COMBINED RAPID TRAVERSE AND SLOW TRAVERSE HYDRAULIC SYSTEM 8 R wk l m Aw T F ,8 M M fi m w 0 V: B 0 q a J AI 3 l 9n FAIU r. w w

Patented Dec. 4, 1934 UNITED STATES COMBINED RAPID TRAVERSE AND SLOW TRAVERSE HYDRAULIC SYSTEM Harry F. Vickers, Detroit, Mich.

Application October 19,

13 Claims.

This invention relates to a combined rapid traverse and slow traverse hydraulic system, and has to do particularly with a hydraulic system requiring a rapid traverse at low pressure and a slow traverse work stroke at high pressure.

The object of the present invention is to provide a plurality of positive displacement pumps, driven at the same speed, in combination with a circuit and automatically controlled valve which furnish a variable flow of fiuid at a minimum loss of power. More specifically, the invention contemplates the combination of two positive displacement pumps with suitable valves and conduits for causing both pumps to deliver into a common conduit up to a predetermined pressure whereupon the flow from one pump is diverted back to the source of supply at substantially no pressure while the other pump continues to deliver into the power conduit at a higher pressure; the direct result being a considerable saving of power on any machine tool or press circuit wherein a rapid traverse to or from a given point at a comparatively low pressure and a much slower traverse at a higher pressure is desired.

In the drawing:

Fig. 1 illustrates a double pump unit and a somewhat diagrammatic circuit for controlling the flow of fluid.

Fig. 2 is a view somewhat similar to Fig. 1 but showing in addition a diagrammatic hook-up of the power cylinder and a speed control valve for controlling the operation of the piston.

In the preferred embodiment of my invention I have shown a relatively small pump 1 and a relatively large pump 2 connected in parallel and operated on a single shaft from a common motor 3. The pumps 1 and 2 are connected by suitable conduits 4 and 5 to a supply tank 6 and in normal operation are adapted to feed the fluid under pressure through conduits 7 and 8 which flow intoa common power line 9.

A low pressure by-pass valve 10 is connected into the conduit 8 and consists of a main passageway, a branch conduit 12, leading to the supply tank 6, an operating piston 13, a spring 14 of predetermined value, and a conduit 15 leading from the pressure conduit 7 into the front face of the piston 13. With this arrangement it will be obvious that when the pressure in the conduit 15 overcomes the pressure of the spring 14, the liquid in the conduit 8 will be conducted back to the supply tank 6 so that there will be substantially no load because of the pump member 2.

A check valve 16 is inserted at a point to pre vent the working or high pressure pump 1 from 1931, Serial No. 569,612

pumping into the open line of the idling pump. A high pressure balanced relief valve 1'7 is connected in between the main power conduit and the main return conduit 18. As shown, this relief valve 17 is of the type shown and described in my copending application Serial No. 552,692, filed July 23, 1931, but it will be understood that any suitable relief valve may be used at this point. It will be obvious that this relief valve will control the working pressure during the slow traverse high pressure stroke of the unit. In this type of valve the balancing is obtained by a plunger 19 and the relieving pressure is determined by an adjustable control valve 20.

In operation, it may be assumed that the pump 1 has a pressure of 200 pounds at h. p., the combined pumps 1 and 2 operating on a rapid traverse at say 20 gallons per minute at 3% h. p. If the spring 14 is set to work at 200 pounds the by-pass valve 10 will open at the beginning of the work or slow traverse stroke, where high pressure is required, and the No. 2 pump will be cut out and will return all liquid pumped therefrom back to the source of supply at substantially no load. The No. 1 pump will now be operating alone and at '700 pounds pressure this pump would give approximatelyGM; gallons per minute using3 h. p.

However, if a single pump is used of 20 gallon capacity, and then using 700 pounds pressure during the work stroke, most of the volume will be going over the relief valve and the pump would still be using approximately 11 h. p. With the arrangement of two pumps working during the rapid traverse stroke only 3%, h. p. is used and during the slow traverse stroke only 3 h. p. is used. The above figures are given as only one example, but it will be readily seen that a large volume pump working during the rapid traverse stroke and cutting out during the high pressure slow traverse stroke will save considerable power and heat on the particular types of installations with which it may be used.

In the modification illustrated in Fig. 2, I have substituted a simple relief valve 21 in place ,of the balanced relief valve 17. I have also shown the system as being connected up with a power cylinder 22 and a conventional valve 23 for controlling the operation of such power cylinder. To the return line 24 of this system I have connected in a speed control valve 25 which will control the speed of movement of the piston in the cylinder 22.

This speed control valve, as shown, is of the type illustrated and described in my copending application Serial No. 543,908, filed June 12, 1931,

' ential across a given sized orifice to positively control the speed of the piston. independently of the load. A'valve 28 is preferably provided for cutting the speed control valve 25 into the sys- 'tem at any 7 by-pass valve 28 may be open while both pumps during the rapid traverse low pressure stroke and being cut in when the piston 13 is actuated to cut out pump No. 2.

Another possible method of operation with the combination shown in Fig. 2 would be the positioning of the regulableorifice control valve 26 which may be set at a certain point to control the speed of the piston and the cylinder 22 during the rapid traverse low pressure stroke and at another point to control the speed of the same piston during the slow traverse high pressure stroke. It will thus be seen that various combiarranged to'be normally nations and methods of operation are possible with the combination shown in Fig. 2 whether either or both pumps are used during either the forward or return stroke of the operating tool, or whether the speed control valve is by-passed or adjusted during part or all of the stroke of the piston in either or both directions. Valve 28 is the valve which may be operated at will to cut the rapid traverse step in and out.

What I claim is:

1. A liquid circulating system comprising in combination a source of liquid supply, a liquid operated motor, a plurality of continuously operating continuously circulating pumps, conduits leading from said pumps for conducting liquid under pressure to said motor, a by-pass valve in one of said conduits adapted to conduct liquid from one of said pumps back to the source of supply, a connection between the discharge side of another pump and said by-pass valve for actuating said by-pass valve and relieving said first named pump only upon the building up of a predetermined pressure in the discharge line of said second named pump, and means for preventing the fluid pressure in the discharge line of said second pump from entering the first named pump or by-pass valve at any time.

2. A system for transmitting power by liquid, comprising a member to be operated at .a relatively high speed and low pressure and also a relatively low speed and high pressure, a source of liquid supply, a relief valve for controlling the pressure during the low speed operation, a plurality of continuously operating and circulating pumps of different volumetric capacity for transmitting the liquid under pressure from said source of supply to the member to be actuated, said pumps combining to supply a relatively large volume of liquid at a relatively low pressure, means in the discharge side of one of said pumps and directly responsive to an increase in said pressure for cutting said pump out of the system and supplying liquid at a high pressure from the other pump, and a one way check valve between the discharge sides of two of said pumps and between said means and liquid operated memher.

3. In a liquid circulating system, the combination of a liquid operated motor of the type having a rapid traverse low pressure stroke and a slow traverse high pressure stroke, a source of liquid supply, a relief valve for controlling the pressure during the slow traverse stroke, a plurality of point desired. In other words, the

1 and 2 are operating-check valve positioned and embodies a regulable orifice outlet valve 26 positive displacement pumps moimted upon the same operating shaft, conduits for conducting, the

liquid under pressure from the plurality of pumps to a single line leading into the motor,means posie tioned in the conduit leading from one of said pumps and directly responsive to a. predetermined I increase in pressure between said pumps and mo-' tor for by passing-the liquid passing through said pump back to the source of supply, and a one way between said means and said single line,

4. In a liquid circulating system of the type having a liquid operated motor having a rapid traverse low pressure stroke and a slow traverse high pressure stroke, the combination of a continuously operating relatively large volume pump and a continuously operating relatively small volume pump, conduits for conducting the liquid under pressure to the motor from both of said pumps during the rapid traverse stroke, means directly responsive to an increase in pressure between the pumps and, motor for automatically returning the liquid passing through the relatively large volume pump back to the source of supply during the slow traverse high pressure stroke of the motor, and a one way check valve positioned between said means and said small volume pump conduit and motor.

5. In a liquid circulating system of the type having a liquid operated motor having a rapid traverse low pressure stroke and a slow traverse high pressure stroke, the combination of a relatively large volume and relatively small volume pump mounted on the same operating shaft, a relief valve for determining the operative pressure during the slow traverse stroke, conduits for conducting the liquid under pressure to the motor from both of said pumps during the rapid traverse stroke, and means responsive to an increase in pressure for automatically returning the liquid passing through the relatively large volume pump back to the source of supply during the slow traverse high pressure stroke of the motor, and a one way check valve positioned between said ioo means and said small volume pump conduit and 20 motor.

6. In a liquid circulating system of the type having a motor designed to be operated at different pressures, the combination of two pumps mounted upon the same operating shaft, a source of supply continuously conducted to said pumps, conduits leading from said pumps to the motor to be operated, a by-pass valve mounted in one conduit and adapted upon operation to conduct the liquid in said conduit back to the source of supply, a connection between the other conduit and said by-pass valve for operating the by-pass valve whereby the one pump is by-passed or returned back to the source of supply depending upon the pressure existing in the conduit leading from the other pump, and a one way check valve between said two conduits.

'7. A system for transmitting power by liquid, comprising a liquid operated motor of the rapid traverse low pressure and slow traverse high pressure type, a source of liquid supply, a plurality of positive displacement pumps of different volumetric capacity connected in between said source of supply and the motor, a by-pass valve connected into the conduit leading from one of said pumps, means for opening said by-pass valve whenever the pressure in the main line leading to the motor exceeds a predetermined point, and a one way check valve between said by-pass valve and main line to the motor.

8. A system for transmitting power by liquid, comprising a liquid operated motor of the rapid traverse low pressure and slow traverse high pressure type, a source of liquid supply, a plu- 'rality of positive displacement pumps of different volumetric capacity connected in between said source of supply and the motor, a relief valve for determining the operative pressure during the slow traverse stroke, a by-pass valve connested into the conduit leading from the pump of largest volumetric capacity, means for opening said by-pass valve whenever the pressure in the main line leading to the motor exceeds a predetermined point, and a one way check valve between said by-pass valve and main line to the motor.

9. A two-volume pump circuit comprising in combination a continuous source ofliquid supply, two positive displacement pumps having different volumetric capacities, means for driving said pumps at a constant speed, conduits for transmitting the liquid under pressure from the pumps to a common operating conduit, the combined liquid in both pumps being transmitted through said common conduit up to a predetermined pressure, means directly responsive to said predetermined pressure to divert liquid from one pump back to the source of supply, and a one way check valve between said means and said common conduit.

10. A system for transmitting power by liquid comprising a plurality of positive displacement pumps of varying volumetric capacities, operated at the same speed, a motor operated by the liquid under pressure from said pumps, means for bypassing one of said pumps out of the-system in accordance with the pressure existing in the system, a check valve positioned between said means and the motor for keeping the fluid pressure existing in said system out of said one pump at any time, and means for controlling the speed of said liquid operated motor.

11. A liquid circulating system comprising in combination a source of liquid supply, a liquid operated motor of the rapid transverse low pressure and slow traverse high pressure type, a plurality of positive displacement pumps for delivering liquid under pressure to the motor, a relief valve for determining the operative pressure during the slow traverse stroke, means operable at a predetermined pressure set up between the pumps and motor for removing the load upon and returning the liquid from one of said pumps back to the source of supply, and a check valve, 0perable upon cutting said one pump out of the system, for keeping the pressure existing in the rest of the system out or said out out pump at any time.

12. In a liquid circulating system, the combination of a liquid operated motor of the type having a rapid traverse low pressure stroke and a slow traverse high pressure stroke, a source 01' liquid supply, a plurality of pumps mounted upon the same operating shaft, a relief valve for determining the operative pressure during the slow traverse stroke, conduits for conducting the liquid under pressure from the plurality of pumps to a single line leading into the motor, means positioned in the conduit leading from one of said pumps for by-passing said pump back to the source of supply when the liquid in the system reaches a predetermined pressure, and means positioned between the by-pass pump conduit and the other conduit or conduits for keeping the fluid pressure existing in the circulating system from entering the by-pass pump conduit at any time.

13. A system for transmitting power by liquid, comprising a work member to be operated at a relatively high speed and low pressure and also at a relatively low speed and high pressure, a source of liquid supply, a continuously operating low pressure pump and a continuously operating high pressure pump for transmitting liquid under pressure from the source of supply to the work member, a conduit leading from the high pressure pump to the work, an unloading valve, a one way check valve, a conduit leading from the low pressure pump through the unloading valve and the one way check valve and joining the first conduit, said two conduits and said pumps combining to supply a relatively large volume of liquid at a relatively low pressure, and a branch conduit connecting the conduit from the high pressure pump to the unloading valve for actuating the same upon development of a predetermined pressure.

HARRY F. VICKERS:

US569612A 1931-10-19 1931-10-19 Combined rapid traverse and slow traverse hydraulic system Expired - Lifetime US1982711A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US569612A US1982711A (en) 1931-10-19 1931-10-19 Combined rapid traverse and slow traverse hydraulic system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US569612A US1982711A (en) 1931-10-19 1931-10-19 Combined rapid traverse and slow traverse hydraulic system

Publications (1)

Publication Number Publication Date
US1982711A true US1982711A (en) 1934-12-04

Family

ID=24276122

Family Applications (1)

Application Number Title Priority Date Filing Date
US569612A Expired - Lifetime US1982711A (en) 1931-10-19 1931-10-19 Combined rapid traverse and slow traverse hydraulic system

Country Status (1)

Country Link
US (1) US1982711A (en)

Cited By (69)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2416860A (en) * 1943-05-08 1947-03-04 Hydraulic Dev Corp Inc Remote control for hydraulic systems
US2419375A (en) * 1942-06-29 1947-04-22 Vickers Inc Power transmission having a plural pump fluid pressure source and a flow-regulating diverting valve
US2472529A (en) * 1946-02-09 1949-06-07 Haahr Poul Hydraulic pump
US2480159A (en) * 1944-08-26 1949-08-30 Odin Corp Power press and fluid control circuit therefor
US2480403A (en) * 1944-08-28 1949-08-30 Oilgear Co Hydraulic transmission
US2484916A (en) * 1944-04-14 1949-10-18 Hpm Dev Corp Valve
US2495785A (en) * 1945-01-11 1950-01-31 Hydraulic Equipment Company Lowering valve
US2518782A (en) * 1946-11-08 1950-08-15 Vickers Inc Power transmission
US2522783A (en) * 1949-04-18 1950-09-19 Goldens Foundry & Machine Comp Hydraulic pump and circuit
US2527458A (en) * 1945-12-21 1950-10-24 Lima Hamilton Corp Hydraulic servomotor mechanism for machine tools
US2530720A (en) * 1944-03-04 1950-11-21 Municipal Supply Company Hydraulic vehicle drive with individual motors for multiple driven parts
US2545260A (en) * 1948-06-03 1951-03-13 Lorne A Cole Apparatus for regulating power used by pulp grinders
US2549897A (en) * 1945-10-18 1951-04-24 Bolinder Munktell Pressure operated valve means for hydrostatic power transmitting systems
US2554930A (en) * 1946-08-15 1951-05-29 Yale & Towne Mfg Co Lift truck
US2579116A (en) * 1947-04-14 1951-12-18 Leland Gifford Co Plural pressure hydraulic feed system
US2604327A (en) * 1946-04-17 1952-07-22 New York Air Brake Co Control valve with flow control
US2608209A (en) * 1947-04-15 1952-08-26 Grove Regulator Company Flow control valve
US2611245A (en) * 1948-05-19 1952-09-23 Allis Chalmers Mfg Co Pump and motor hydraulic system and regulating apparatus therefor
US2617389A (en) * 1949-10-07 1952-11-11 Niagara Machine And Tool Works Hydraulic press control system
US2618932A (en) * 1949-09-09 1952-11-25 Vickers Inc Pump and motor hydraulic system, including multiple pumps
US2624283A (en) * 1949-01-05 1953-01-06 Leland Gifford Co Hydraulic pump
US2625797A (en) * 1952-03-15 1953-01-20 Dake Engine Company Hydraulic eductor valve
US2630566A (en) * 1950-02-09 1953-03-10 Fmc Corp High-speed lidder
US2632459A (en) * 1947-12-11 1953-03-24 Heald Machine Co Control apparatus for hydraulic systems
US2655930A (en) * 1950-08-24 1953-10-20 Electraulic Presses Ltd Unloading and relief valve
US2656445A (en) * 1948-06-23 1953-10-20 Odin Corp Welding machine and control and actuating mechanism
US2677238A (en) * 1949-05-02 1954-05-04 Greer Hydraulics Inc Hydraulic motor and system
US2690127A (en) * 1950-02-20 1954-09-28 Sinclair Harold Speed and frequency governor
US2728194A (en) * 1954-03-29 1955-12-27 Vickers Inc Control circuit for hydraulic power transmission
US2767688A (en) * 1946-12-26 1956-10-23 Harris Seybold Co Hydraulically actuated multiple spindle paper drill
US2769394A (en) * 1949-10-21 1956-11-06 Borg Warner Power unit
US2781727A (en) * 1950-03-15 1957-02-19 Bendix Aviat Corp Pump apparatus
US2846848A (en) * 1955-05-16 1958-08-12 Caterpillar Tractor Co Fluid pressure system and control
US2852918A (en) * 1954-12-24 1958-09-23 New York Air Brake Co Hydraulic control circuit with unloading means
US2904957A (en) * 1954-08-03 1959-09-22 Yale & Towne Mfg Co Hydraulic drive for industrial truck
US2912906A (en) * 1955-09-09 1959-11-17 Cincinnati Milling Machine Co Machine tool transmission
US2917897A (en) * 1955-02-04 1959-12-22 Walter M Shaffer Hydraulic drive mechanism
US2927558A (en) * 1956-01-16 1960-03-08 American Brake Shoe Co Hydraulic press and control means
US2932167A (en) * 1959-03-02 1960-04-12 Vickers Inc Power transmission
US2963865A (en) * 1959-07-07 1960-12-13 Ethyl Corp Cyclic extrusion apparatus
US2973914A (en) * 1956-02-16 1961-03-07 H G Weber And Company Inc Roll stand
US2993393A (en) * 1957-05-29 1961-07-25 Kendall Edgar Homer Edge roll control for wheel rolling mills
US3018902A (en) * 1955-12-06 1962-01-30 Manning Maxwell & Moore Inc Hydraulic crane
US3022757A (en) * 1960-04-22 1962-02-27 Carroli C Clough Tank head dishing mechanism
US3025725A (en) * 1949-08-09 1962-03-20 Clifton R Roche Transmission construction
US3030900A (en) * 1958-04-11 1962-04-24 Niagara Machine & Tool Works Hydraulic seamer
US3061032A (en) * 1957-03-29 1962-10-30 Allgaier Werke Gmbh Hydraulic installation for vehicles such as tractors and the like
US3064426A (en) * 1959-06-22 1962-11-20 Dba Sa Hydraulic systems
US3083847A (en) * 1958-04-26 1963-04-02 Marini Luigi Load transferring installation
US3084513A (en) * 1960-03-08 1963-04-09 Gen Controls Co Electrohydraulic actuator
US3088688A (en) * 1958-09-25 1963-05-07 H G Weber And Company Inc Hydraulic system
US3120171A (en) * 1958-01-28 1964-02-04 Acme Steel Co Automatic strapping machine
US3156098A (en) * 1959-11-20 1964-11-10 Ford Motor Co Hydraulic power system
US3173258A (en) * 1962-10-17 1965-03-16 Applied Power Ind Inc Control system for hydrostatic transmission circuits
US3185175A (en) * 1962-12-03 1965-05-25 Allis Chalmers Mfg Co Directional hydraulic control valve
US3187508A (en) * 1964-06-29 1965-06-08 Miehle Goss Dexter Inc Hydraulic clamp system for guillotine cutters
US3188890A (en) * 1958-02-06 1965-06-15 Kearney & Trecker Corp Car wheel borer with transfer mechanism
US3204410A (en) * 1962-11-28 1965-09-07 Hydraulic Unit Specialities Co Hydrostatic drive and control means therefor
DE1209431B (en) * 1961-05-04 1966-01-20 Garbe Lahmeyer & Co Ag Pressure medium circuit with two pressure medium producers
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3357179A (en) * 1966-01-14 1967-12-12 Gen Precision Inc Actuation system
US3540218A (en) * 1969-05-12 1970-11-17 Gen Signal Corp Hydraulic supply system with two pumping units
US3857336A (en) * 1972-04-26 1974-12-31 Sybron Corp Automatic filtermass press
US3889586A (en) * 1972-08-24 1975-06-17 Usm Corp Control for fluid pressure actuators
US3968811A (en) * 1974-05-16 1976-07-13 Societe Anonyme: Poclain Pressurized fluid control circuit
US4002027A (en) * 1973-10-01 1977-01-11 Tyrone Hydraulics, Inc. Multiple pump control system
US4245964A (en) * 1978-11-08 1981-01-20 United Technologies Corporation Efficiency fluid pumping system including sequential unloading of a plurality of pumps by a single pressure responsive control valve
US4609330A (en) * 1985-04-04 1986-09-02 Federal Supply And Equipment Company Modular unloading sequencing switching valve assembly for hydraulic system
DE102012011953A1 (en) * 2012-06-18 2013-12-19 Christian Böhner Device for generating different working pressures

Cited By (71)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2419375A (en) * 1942-06-29 1947-04-22 Vickers Inc Power transmission having a plural pump fluid pressure source and a flow-regulating diverting valve
US2416860A (en) * 1943-05-08 1947-03-04 Hydraulic Dev Corp Inc Remote control for hydraulic systems
US2530720A (en) * 1944-03-04 1950-11-21 Municipal Supply Company Hydraulic vehicle drive with individual motors for multiple driven parts
US2484916A (en) * 1944-04-14 1949-10-18 Hpm Dev Corp Valve
US2480159A (en) * 1944-08-26 1949-08-30 Odin Corp Power press and fluid control circuit therefor
US2480403A (en) * 1944-08-28 1949-08-30 Oilgear Co Hydraulic transmission
US2495785A (en) * 1945-01-11 1950-01-31 Hydraulic Equipment Company Lowering valve
US2549897A (en) * 1945-10-18 1951-04-24 Bolinder Munktell Pressure operated valve means for hydrostatic power transmitting systems
US2527458A (en) * 1945-12-21 1950-10-24 Lima Hamilton Corp Hydraulic servomotor mechanism for machine tools
US2472529A (en) * 1946-02-09 1949-06-07 Haahr Poul Hydraulic pump
US2604327A (en) * 1946-04-17 1952-07-22 New York Air Brake Co Control valve with flow control
US2554930A (en) * 1946-08-15 1951-05-29 Yale & Towne Mfg Co Lift truck
US2518782A (en) * 1946-11-08 1950-08-15 Vickers Inc Power transmission
US2767688A (en) * 1946-12-26 1956-10-23 Harris Seybold Co Hydraulically actuated multiple spindle paper drill
US2579116A (en) * 1947-04-14 1951-12-18 Leland Gifford Co Plural pressure hydraulic feed system
US2608209A (en) * 1947-04-15 1952-08-26 Grove Regulator Company Flow control valve
US2632459A (en) * 1947-12-11 1953-03-24 Heald Machine Co Control apparatus for hydraulic systems
US2611245A (en) * 1948-05-19 1952-09-23 Allis Chalmers Mfg Co Pump and motor hydraulic system and regulating apparatus therefor
US2545260A (en) * 1948-06-03 1951-03-13 Lorne A Cole Apparatus for regulating power used by pulp grinders
US2656445A (en) * 1948-06-23 1953-10-20 Odin Corp Welding machine and control and actuating mechanism
US2624283A (en) * 1949-01-05 1953-01-06 Leland Gifford Co Hydraulic pump
US2522783A (en) * 1949-04-18 1950-09-19 Goldens Foundry & Machine Comp Hydraulic pump and circuit
US2677238A (en) * 1949-05-02 1954-05-04 Greer Hydraulics Inc Hydraulic motor and system
US3025725A (en) * 1949-08-09 1962-03-20 Clifton R Roche Transmission construction
US2618932A (en) * 1949-09-09 1952-11-25 Vickers Inc Pump and motor hydraulic system, including multiple pumps
US2617389A (en) * 1949-10-07 1952-11-11 Niagara Machine And Tool Works Hydraulic press control system
US2769394A (en) * 1949-10-21 1956-11-06 Borg Warner Power unit
US2630566A (en) * 1950-02-09 1953-03-10 Fmc Corp High-speed lidder
US2690127A (en) * 1950-02-20 1954-09-28 Sinclair Harold Speed and frequency governor
US2781727A (en) * 1950-03-15 1957-02-19 Bendix Aviat Corp Pump apparatus
US2655930A (en) * 1950-08-24 1953-10-20 Electraulic Presses Ltd Unloading and relief valve
US2625797A (en) * 1952-03-15 1953-01-20 Dake Engine Company Hydraulic eductor valve
US2728194A (en) * 1954-03-29 1955-12-27 Vickers Inc Control circuit for hydraulic power transmission
US2904957A (en) * 1954-08-03 1959-09-22 Yale & Towne Mfg Co Hydraulic drive for industrial truck
US2852918A (en) * 1954-12-24 1958-09-23 New York Air Brake Co Hydraulic control circuit with unloading means
US2917897A (en) * 1955-02-04 1959-12-22 Walter M Shaffer Hydraulic drive mechanism
US2846848A (en) * 1955-05-16 1958-08-12 Caterpillar Tractor Co Fluid pressure system and control
US2912906A (en) * 1955-09-09 1959-11-17 Cincinnati Milling Machine Co Machine tool transmission
US3018902A (en) * 1955-12-06 1962-01-30 Manning Maxwell & Moore Inc Hydraulic crane
US2927558A (en) * 1956-01-16 1960-03-08 American Brake Shoe Co Hydraulic press and control means
US2973914A (en) * 1956-02-16 1961-03-07 H G Weber And Company Inc Roll stand
US3061032A (en) * 1957-03-29 1962-10-30 Allgaier Werke Gmbh Hydraulic installation for vehicles such as tractors and the like
US2993393A (en) * 1957-05-29 1961-07-25 Kendall Edgar Homer Edge roll control for wheel rolling mills
US3120171A (en) * 1958-01-28 1964-02-04 Acme Steel Co Automatic strapping machine
US3188890A (en) * 1958-02-06 1965-06-15 Kearney & Trecker Corp Car wheel borer with transfer mechanism
US3030900A (en) * 1958-04-11 1962-04-24 Niagara Machine & Tool Works Hydraulic seamer
US3083847A (en) * 1958-04-26 1963-04-02 Marini Luigi Load transferring installation
US3088688A (en) * 1958-09-25 1963-05-07 H G Weber And Company Inc Hydraulic system
US2932167A (en) * 1959-03-02 1960-04-12 Vickers Inc Power transmission
DE1174166B (en) * 1959-03-02 1964-07-16 Sperry Rand Corp A control device for hydraulic servomotors with two pumps connected in parallel
US3064426A (en) * 1959-06-22 1962-11-20 Dba Sa Hydraulic systems
US2963865A (en) * 1959-07-07 1960-12-13 Ethyl Corp Cyclic extrusion apparatus
US3156098A (en) * 1959-11-20 1964-11-10 Ford Motor Co Hydraulic power system
US3084513A (en) * 1960-03-08 1963-04-09 Gen Controls Co Electrohydraulic actuator
US3022757A (en) * 1960-04-22 1962-02-27 Carroli C Clough Tank head dishing mechanism
DE1209431B (en) * 1961-05-04 1966-01-20 Garbe Lahmeyer & Co Ag Pressure medium circuit with two pressure medium producers
US3173258A (en) * 1962-10-17 1965-03-16 Applied Power Ind Inc Control system for hydrostatic transmission circuits
US3204410A (en) * 1962-11-28 1965-09-07 Hydraulic Unit Specialities Co Hydrostatic drive and control means therefor
US3185175A (en) * 1962-12-03 1965-05-25 Allis Chalmers Mfg Co Directional hydraulic control valve
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3187508A (en) * 1964-06-29 1965-06-08 Miehle Goss Dexter Inc Hydraulic clamp system for guillotine cutters
US3357179A (en) * 1966-01-14 1967-12-12 Gen Precision Inc Actuation system
US3540218A (en) * 1969-05-12 1970-11-17 Gen Signal Corp Hydraulic supply system with two pumping units
US3857336A (en) * 1972-04-26 1974-12-31 Sybron Corp Automatic filtermass press
US3889586A (en) * 1972-08-24 1975-06-17 Usm Corp Control for fluid pressure actuators
US4002027A (en) * 1973-10-01 1977-01-11 Tyrone Hydraulics, Inc. Multiple pump control system
US3968811A (en) * 1974-05-16 1976-07-13 Societe Anonyme: Poclain Pressurized fluid control circuit
US4245964A (en) * 1978-11-08 1981-01-20 United Technologies Corporation Efficiency fluid pumping system including sequential unloading of a plurality of pumps by a single pressure responsive control valve
US4609330A (en) * 1985-04-04 1986-09-02 Federal Supply And Equipment Company Modular unloading sequencing switching valve assembly for hydraulic system
DE102012011953A1 (en) * 2012-06-18 2013-12-19 Christian Böhner Device for generating different working pressures
DE102012011953B4 (en) * 2012-06-18 2017-04-13 Böhner-EH GmbH Hydraulic device for generating different flow rates with different working pressures and using such device in a hydraulic system

Similar Documents

Publication Publication Date Title
US2301028A (en) Power transmission
EP0249154B1 (en) Hydraulic pressure system
US2961829A (en) Hydraulic transmission
US2214817A (en) Power transmission
US2336911A (en) Power transmission and steering control for traction devices
US2253617A (en) Power transmission
US3856436A (en) Power transmission
US4436487A (en) Foam liquid concentrate supply system
US3723025A (en) Variable bypass for fluid power transfer systems
US4481769A (en) Control system for hydraulically driven vehicles
US5522212A (en) Rod equal displacement cylinder in a rapid transfer and feed system
US2307544A (en) Power transmission
US3612202A (en) Hydrostatic wheel assist
CN101094999B (en) Hydrostatic drive with speed limitation
US20090064676A1 (en) Hydrostatic drive having volumetric flow equalisation
US4819430A (en) Variably charged hydraulic circuit
US2218565A (en) Compound positive displacement pump circuit
US2210144A (en) Hydraulic control apparatus
DE10303487A1 (en) Regulation for a hydrostatic transmission
GB1068863A (en) Improvements in or relating to reciprocating pumps
US4402181A (en) Hydraulic drive system for a vehicle
US2643516A (en) Fluid pressure system
GB1415767A (en) Hydraulic transmissions for driving machines provided with holding brakes
GB1369530A (en) Hydraulic system for hydraulically tiltable boat propeller drive units
US2768582A (en) Power transmission