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US3382669A - Hydraulic booster apparatus - Google Patents

Hydraulic booster apparatus Download PDF

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Publication number
US3382669A
US3382669A US552743A US55274366A US3382669A US 3382669 A US3382669 A US 3382669A US 552743 A US552743 A US 552743A US 55274366 A US55274366 A US 55274366A US 3382669 A US3382669 A US 3382669A
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Prior art keywords
fluid
pressure
valve
line
hydraulic
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US552743A
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English (en)
Inventor
Alajos Z Bauer
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FCI USA LLC
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Burndy Corp
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Publication date
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Priority to US552743A priority Critical patent/US3382669A/en
Priority to ES340803A priority patent/ES340803A1/es
Priority to FR107167A priority patent/FR1525463A/fr
Priority to CH720067A priority patent/CH463166A/fr
Priority to GB23895/67A priority patent/GB1143142A/en
Priority to SE07180/67A priority patent/SE325840B/xx
Priority to DE19671625015 priority patent/DE1625015A1/de
Priority to NL6707161.A priority patent/NL155479B/xx
Priority to BE698957D priority patent/BE698957A/xx
Application granted granted Critical
Publication of US3382669A publication Critical patent/US3382669A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/22—Control arrangements for fluid-driven presses controlling the degree of pressure applied by the ram during the pressing stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • 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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3052—Shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member

Definitions

  • HYDRAULIC BOOSTER APPARATUS Filed May 25, 1966 2 Sheets-Sheet l E SM E May 14, 1968 A. z. BAUER 3,382,669 HYDRAULIC BOOSTER APPARATUS Filed May 25, 1966 2 Sheets-Sheet 2 /Qg U ik y .1"
  • a hydraulic apparatus for operating devices such as portable crimping tools, which is designed independently of a fluid pressure source and reservoir so that it may be attached conveniently to an external source and reservoir such as are found in common use on aerial lift trucks.
  • the apparatus includes a hydraulic booster pump which is adapted to be driven by the fluid pressure derived from the external source, and control valve means together with a pressure reducing valve which will permit selective operation of the booster pump so as to supply either reduced pressure or boosted pressure to the utilization device.
  • This invention relates to a hydraulic booster apparatus, and more particularly to an apparatus which can be connected to an existing hydraulic system to generate and control sufficient pressure for operating various devices, such as an electrical connector crimping tool.
  • hydraulic compression tools of the type used in securing electrical connectors to power lines commonly require pressure to be supplied at two different values on an alternate, selective basis. That is, a first pressure of 100 p.s.i. might be used to gently grip a connector between the jaws of the tool during an initial positioning operation, and a second pressure of 10,000 p.s.i. might be used for full compression force.
  • FIGURE 1 is a diagrammatic layout of a hydraulic ICC booster system assembled in accordance with this invention
  • FIGURE 2 is a schematic representation of the control value of the system of FIGURE l, shown in the HOLD position; y
  • FIGUR-E 3 represents the control of FIGURE 2 in the OFF position
  • FIGURE 4 is a schematic representation of the output and control valve portions of the system of FIGURE 1 showing modiiications thereof;
  • FIGURE 5 is a pictorial representation of how a system of the type here disclosed might be carried on a commercial boom and bucket
  • the hydraulic booster system of this invention may be seen to comprise generally the operating elements 10 (enclosed within the dotted envelope) which are provided with a fluid input line 12, an output line 14, and a reservoir return line 16.
  • the operating elements 10 include as basic equipment, a control valve 20 and a pumping unit 10; associated with the pumping unit are a shuttle valve 50, a pressure relief valve 60, a check valve 70, and a pressure reducing valve 80.
  • input line 12 would be connected to the high pressure hydraulic line (not shown) of an available hydraulic system in, for example, a hydraulically operated lift or boom truck.
  • Reservoir return line 16 would in turn be connected to the fluid storage reservoir of such an available system in order to provide a complete flow path for the overall system of the invention.
  • Commercially available iluid coupling devices of the quickdisconnect type might preferably be used for establishing these connections.
  • output line 14 would be coupled to a hydraulic crimping tool or other such device for utilizing the uid pressure output of this invention.
  • Operation of the system illustrated in FIGURE 1 may be brielly described as follows: Overall operation is manually controlled by the position of control lever 21 on control valve 20. Three positions are provided, namely OFF, HOLD and CRIMP. In the OFF position shown in FIGURE 3, the ilow of liuid from input line 12 is completely cut off at valve 20, and the pressure in all other lines of the system is allowed to drain to the reservoir pressure in return line 16. In the HOLD position shown in FIGURE 2, lluid at 1500 psi. from line 12, is applied to pressure reducing valve 80. ri ⁇ his valve reduces the 1500 p.s.i.
  • valve 20 applies 1500 p.s.i. pressure from line 12 through line 23 directly to shuttle valve 50'. This starts and operates the pump portion 45 of pumping unit 40. Operation of pump portion 46 raises or boosts the fluid pressure in output portion 42 of the pumping unit 40, from 100 p.s.i. to approximately 10,000 p.s.i. and forces this high pressure fluid into output line 14. Manipulation of valve 20 thus permits the pressure in output line 14 to be varied selectively from reservoir pressure to p.s.i. and to 1500 p.s.i.
  • FIGURE 1 A detailed explanation of fluid flow in this system during crimping operation may best be understood by reference to FIGURE 1.
  • input port P1 is internally coupled to both of output ports P2 and P3, and exhaust port P4 is effectively sealed.
  • Fluid from line 12, at 1500 p.s.i. pressure, is thus applied to rcducingvalve 30, through line 22 which extends from port P2, and to shuttle valve 50, through line 23 which extends from port P3.
  • assassa Shuttle valve 50 ⁇ is a two-way, two-position iluid valve which is provided with an inlet line 23, two outlet lines 51 and 52, and an exhaust line 53. It operates in a wellknown manner to connect one outlet line to the inlet line and the other outlet line to the exhaust line, and to alternately reverse these connections in response to the position of shuttle arm d.
  • the position of shuttle arm 54 is controlled by extension rod 47 which is coupled at one end to arm 54 and at the other end to pump plunger 49. Rod 47 and plunger 49' are in turn positioned by iluid forces acting on pump piston 48 which is mounted to rod 47. For example, with arm 54 in the position shown in FIGURE 1, iiuid from line 23 at 1500 p.s.i.
  • the reciprocating operation described above drives plunger 49 alternately into and out of compression charnber 43 within output portion 4Z of pumping unit 46.
  • Chamber 43 is kept continuously illed with hydraulic fluid supplied through check valve 70 and check valve feed line 72.
  • plunger d As plunger d nowadays enters chamber 43, it tends to compress the fluid which is trapped within the chamber by the one-way dow characteristics of check -valve 70.
  • the pressure of the entrapped fluid becomes high enough, it acts to unseat valve head 44 against the load imposed by valve spring 4S, and permits the lluid to flow through passages 41 in valve head 44 into valve cylinder 38 and then into output line 14.
  • the characteristics of plunger 49, chamber 43 and valve loading spring 45 may thus he chosen to produce a desired hydraulic pressure (such as 10,000 p.s.i.), in the uid which passes through valve cylinder 38 into output line 14.
  • FIGURE 2 illustrates duid low and internal connections for control valve 2d in the HGLD position.
  • ports P4 and P3 are closed, and input port P1 is internally connected to port P2.
  • port 173 there is no iluid flow in line 23, so that shuttle valve 5d and pumping unit d@ will not operate.
  • 1500 p.s.i. iluid from line 12 will be supplied to pressure reducing valve 30 through ports P1 and P2 and line 22.
  • 100 p.s.i. vad will pass from the pressure reducing valve E50 to check valve 7d and then to compression char ber 43 in output portion 42 of pumping unit 4d.
  • Valve head 44 will then unseat under the 100 p.s.i. pressure, and by-pass passages 41 in valve head t4 will permit the 100 p.s.i. duid in chamber 43 to dow into line 14.
  • valve 2d In the OFF position of control valve 2d, schematically illustrated in FIGURE 3, input port P1 is closed to shut off iiuid flow through line 12, and ports P2 and P3 are internally connected to exhaust port P4.
  • the internal connections established by the OFF position of valve 2li permit the fluid in lines 14, 22 and 23 to return to the reservoir pressure level of lines 16 and 16'.
  • pressure in output line 1li In the OFF condition of the system, pressure in output line 1li is drained olf to line 16 through operation of pressure relief valve 60.
  • pressure relier valve 6@ include a spring loaded safety valve portion and a spring-andpiston operated drain valve portion 62.
  • the input iluid sides of portions and 62 are cach coupled to valve cylinder 38 in pumping unit 4t) by a common passage 63.
  • the output tluid sides of both of these portions are coupled by a common passage 64 directly to exhaust branch line 16.
  • Safety valve portion 61 operates in conventional manner to exhaust fluid from passage 63 into exhaust branch 16 whenever the pressure in cylinder 38 exceeds a predetermined maximum value. Operation of drain valve portion 62 on the other hand, is controlled by duid pressure applied to valve piston 65. Drain valve portion 62 may be moved left or right to respectively open or obstruct connecting passage 67 which couples passage 63 to passage 64.-.
  • a branch 2?.' of line 22 subjects the left face of drain valve piston 65 to the duid pressure which exists in line 22.
  • FIGURE 4 illustrates modications and additions which may be embodied into the system of FIGURE 1 within the scope of this invention. Elements shown in this ligure which have corresponding counterparts in FIGURE l are denoted by identical reference numerals increased by 160. Thus, for example, control valve 120 in FIGURE 4 corresponds generally to control valve 20 in FIGURE l. In the embodiment illustrated in FIGURE 4, the control lever on control valve 120 has been replaced by a pneumatic actuator 118. This actuator may comprise any well known form of pneumatically powered drive mechanism capable of producing at least intermittent arcuate motion to rotate the shaft of valve 120.
  • a mechanism of this type could be activated 'by a hand-held squeeze-bulb such as 119 which might be coupled to actuator 118 by a liexible pneumatic tube 117 of convenient length.
  • a hand-held squeeze-bulb such as 119 which might be coupled to actuator 118 by a liexible pneumatic tube 117 of convenient length.
  • Such an actuator assembly would permit an operator to control a system of the type described accurately and conveniently, using non-conductive, non-electrical means, from a remote location.
  • FIGURE 4 further illustrates means for permitting the selection of either one of two different maximum output pressures in a system of the type disclosed.
  • a pressure selector valve is posi- -tioned in the system interposed between pump output line 114 and nal output lines 114e and 1141).
  • the selector valve would be provided with input pressure from line 114 at a maximum value of, say 10,000 p.s.i.
  • the input pressure may be passed directly through to line 114a with no reduction in value, or may be internally routed through a reducing portion (not detailed) within valve 115, before passing to line 11427 at a reduced value of, for example, 6,000 psi.
  • a connection to exhaust line branch 116 through sub branch 116 is provided to allow for any overflow or backup conditions within the valve. It can now be seen that a commercially available selector valve of this type, incorporated into the system of FIGURE l would substantially enhance the versatility and llexibility of such a system.
  • Such a case might be provided with one of more separabie hydraulic connectors 92 so that it could be conveniently carried into and mounted to a platform or bucket 94 on the aerial boom arm 9'1 of a lift truck (not shown).
  • a hydraulic booster apparatus for attachment to a separately existing hydraulic fluid system which has a pressurized hydraulic outlet port, said apparatus compn'sing:
  • first fluid conduit means forming a hydraulic fluid passage which is attacha'ble at a second end thereof to a hydraulic fluid utilization device
  • said hydraulic fluid pumping-unit having an inlet directed toward the said first end of said fluid passage and an outlet directed toward the said second end of said fluid passage and being operable selectively to increase the pressure of fluid in said fluid passage from a given pressure at the inlet to a greater pressure at the outlet;
  • a fluid-driven motive power source operatively coupled to said pumping unit to permit selective operation of said pumping unit
  • second fluid conduit means forming a hydraulicfluid passage between said fluid flow control valve and said fluid-driven motive power source for supplying fluid to drive said motive power source;
  • control Valve being operable to selectively block and permit fluid through said first conduit means to the said second end thereof, and to simultaneously block and permit fluid flow through said second conduit means to said fluid-driven motive power source for causing selective operation of said pumping-unit;
  • said apparatus may be made to deliver fluid from said separately existing hydraulic fluid system to said utilization device selectively, with or without increased pressure, in response to the operation of said fluid flow control valve.
  • -A hydraulic booster apparatus in accordance with claim 1, further including a pressure-reducing valve means interposed in said first conduit means between the said first end thereof and the said pumping unit, for reducing the pressure of the fluid obtained from said separately existing hydraulic system from an initial pressure to a lower pressure before said fluid is supplied to the said inlet of said pumping-unit.
  • a one-Way check-valve interposed in said first conduit means between said pressure reducing valve means and said pumping unit, for limiting fluid flow to the direction from said reducing valve means to said pumping-unit only;
  • auxiliary conduit means coupled at a first end thereof to the inlet part of said separately existing hydraulic fluid system and coupled at a second end thereof to said first conduit means between said one-way checkvalve and the said second end of said first conduit means for returning fluid to said fluid storage reservoir;
  • a hydraulic booster apparatus for attachment to a separately existing hydraulic fluid system which has a pressurized hydraulic fluid outlet port and a fluid storage reservoir with an inlet port for receiving returned fluid, said apparatus comprising:
  • first fluid conduit means forming a hydraulic fluid passage which is attachable at a first end thereof to the pressurized hydraulic fluid outlet port of a hydraulic fluid system and is attachable at a second end thereof to a hydraulic fluid utilization device;
  • said hydraulic fluid pumping-unit having an inlet directed toward the said first end of said fluid passage and an outlet directed toward the said second end of said fluid passage and 'being operable selectively to increase the pressure of fluid in said fluid passage from a given pressure at the inlet to a greater pressure at the outlet;
  • a fluid-driven reciprocating motive power source including a shuttle Valve means, operatively coupled to said pumping-unit to permit selective operation of said pumping-unit and adapted to be driven by hydraulic fluid pressure obtained from said hydraulic fluid system through said first conduit means;
  • a fluid-flow control Valve having first, second and third operating positions, interposed in said first conduit means between the said first end of said fluid passage and the said pumping-uit;
  • pressure-reducing valve means interposed in said first conduit means between the said rst end thereof and the said pumping-unit, for reducing the pressure of the fluid obtained from said separately existing hydraulic system from an initial pressure to a lower pressure before said fluid is supplied to the said inlet of said pumping-unit;
  • auxiliary conduit means having a first end thereof coupled to the inletport of said separately existing hydraulic fluid system and a second end thereof coupled to said first conduit means fbetween said one-way check-valve and the said second end of said first conduit means for returning fluid to the said fluid storage reservoir;
  • a pressure operated relief valve means interposed in said auxiliary conduit means between the said first and second ends of said auxiliary conduit means for selectively controlling the return of fluid from said first conduit means to the said fluid storage reservoir;
  • fluid passage means operatively coupling said pressure-operated relief valve means to said first conduit means intermediate said fluid flow control valve means and said one-way check-valve for supplying uid pressure to operate said relief valve in response to the position of said fluid ow control valve means;
  • the said first position of said lluid low control valve means ⁇ being adapted to -block iluid flow from the rst end of said first conduit means and to provide fluid flow passage means coupling said irst and second outlets to said third outlet for returning uid from said apparatus to said fluid storage reservoir;
  • the said second position of said fluid flow control valve means being adapted to block fluid ow from said second and third outlets and to provide fluid tlow passage means coupling said inlet to said outlet for permitting iluid ow from said rst end to said second end of said conduit means;
  • the said third position of said uid flow control valve means being adapted to block fluid ow through said third outlet and to provide uid ow passage means coupling said inlet to said rst and second outlets for permitting fluid llow through said first conduit means and for supplying fluid pressure to operate said reciprocating motive power source.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fluid-Pressure Circuits (AREA)
US552743A 1966-05-25 1966-05-25 Hydraulic booster apparatus Expired - Lifetime US3382669A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US552743A US3382669A (en) 1966-05-25 1966-05-25 Hydraulic booster apparatus
ES340803A ES340803A1 (es) 1966-05-25 1967-05-20 Un aparato elevador hidraulico.
FR107167A FR1525463A (fr) 1966-05-25 1967-05-22 Surpresseur hydraulique
GB23895/67A GB1143142A (en) 1966-05-25 1967-05-23 Hydraulic pressure change apparatus
CH720067A CH463166A (fr) 1966-05-25 1967-05-23 Dispositif d'amplification de pression
SE07180/67A SE325840B (fr) 1966-05-25 1967-05-23
DE19671625015 DE1625015A1 (de) 1966-05-25 1967-05-23 Hydraulische Verstaerkervorrichtung
NL6707161.A NL155479B (nl) 1966-05-25 1967-05-24 Inrichting voor het wijzigen van de druk uit een persvloeistofnet.
BE698957D BE698957A (fr) 1966-05-25 1967-05-24

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US552743A US3382669A (en) 1966-05-25 1966-05-25 Hydraulic booster apparatus

Publications (1)

Publication Number Publication Date
US3382669A true US3382669A (en) 1968-05-14

Family

ID=24206620

Family Applications (1)

Application Number Title Priority Date Filing Date
US552743A Expired - Lifetime US3382669A (en) 1966-05-25 1966-05-25 Hydraulic booster apparatus

Country Status (8)

Country Link
US (1) US3382669A (fr)
BE (1) BE698957A (fr)
CH (1) CH463166A (fr)
DE (1) DE1625015A1 (fr)
ES (1) ES340803A1 (fr)
GB (1) GB1143142A (fr)
NL (1) NL155479B (fr)
SE (1) SE325840B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0156939A1 (fr) * 1982-10-26 1985-10-09 Mora Hydraulics AB Outil dirigé par pression
US4776641A (en) * 1986-12-20 1988-10-11 Daimler-Benz Aktiengesellschaft Apparatus for the protection of a hydraulic brake system of a road vehicle against an evaporation of the brake fluid
US20050178121A1 (en) * 2004-02-16 2005-08-18 Leif Hansen Hydraulic tool

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008003500U1 (de) * 2008-03-12 2009-07-30 Wagner Vermögensverwaltungs-GmbH & Co. KG Hydraulische Druckliefereinheit für einen Kraftschrauber

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US886379A (en) * 1907-10-21 1908-05-05 Laurits Aksel Laursen Automatic hydraulic pump.
US1332340A (en) * 1919-01-16 1920-03-02 Robert A Horne Fluid-pressure power means for presses
US1888990A (en) * 1929-08-16 1932-11-29 Economy Fuse And Mfg Co Automatically controlled hydraulic press intensifier
US2080695A (en) * 1934-12-10 1937-05-18 Cargile Clifton Pressure accumulator
US2608059A (en) * 1948-07-22 1952-08-26 Kux Machine Company Hydraulic pressure booster
GB768258A (en) * 1954-06-08 1957-02-13 Fawcett Preston & Co Ltd Improvements in or relating to hydraulic pressure intensifiers or boosters
US2867088A (en) * 1955-04-22 1959-01-06 Kux Machine Company Pressure multiplier
US3041975A (en) * 1960-05-26 1962-07-03 Applied Power Ind Inc Fluid actuated hydraulic power unit
US3186173A (en) * 1960-09-15 1965-06-01 American Mach & Foundry Variable pressure hydraulic system

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US886379A (en) * 1907-10-21 1908-05-05 Laurits Aksel Laursen Automatic hydraulic pump.
US1332340A (en) * 1919-01-16 1920-03-02 Robert A Horne Fluid-pressure power means for presses
US1888990A (en) * 1929-08-16 1932-11-29 Economy Fuse And Mfg Co Automatically controlled hydraulic press intensifier
US2080695A (en) * 1934-12-10 1937-05-18 Cargile Clifton Pressure accumulator
US2608059A (en) * 1948-07-22 1952-08-26 Kux Machine Company Hydraulic pressure booster
GB768258A (en) * 1954-06-08 1957-02-13 Fawcett Preston & Co Ltd Improvements in or relating to hydraulic pressure intensifiers or boosters
US2867088A (en) * 1955-04-22 1959-01-06 Kux Machine Company Pressure multiplier
US3041975A (en) * 1960-05-26 1962-07-03 Applied Power Ind Inc Fluid actuated hydraulic power unit
US3186173A (en) * 1960-09-15 1965-06-01 American Mach & Foundry Variable pressure hydraulic system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0156939A1 (fr) * 1982-10-26 1985-10-09 Mora Hydraulics AB Outil dirigé par pression
US4776641A (en) * 1986-12-20 1988-10-11 Daimler-Benz Aktiengesellschaft Apparatus for the protection of a hydraulic brake system of a road vehicle against an evaporation of the brake fluid
US20050178121A1 (en) * 2004-02-16 2005-08-18 Leif Hansen Hydraulic tool
US7204087B2 (en) * 2004-02-16 2007-04-17 Minibooster Hydraulics A/S Hydraulic tool

Also Published As

Publication number Publication date
DE1625015A1 (de) 1969-10-23
DE1625015B2 (fr) 1971-02-04
ES340803A1 (es) 1968-06-16
BE698957A (fr) 1967-11-24
SE325840B (fr) 1970-07-06
GB1143142A (en) 1969-02-19
NL6707161A (fr) 1967-11-27
NL155479B (nl) 1978-01-16
CH463166A (fr) 1968-09-30

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