US3928969A - Self-monitored fluid pressure booster system - Google Patents

Self-monitored fluid pressure booster system Download PDF

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Publication number
US3928969A
US3928969A US473217A US47321774A US3928969A US 3928969 A US3928969 A US 3928969A US 473217 A US473217 A US 473217A US 47321774 A US47321774 A US 47321774A US 3928969 A US3928969 A US 3928969A
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US
United States
Prior art keywords
pressure
fluid
motor
pump
sliding
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
US473217A
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English (en)
Inventor
Franck Picker
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.)
OAK RIDGE MACHINES
Original Assignee
OAK RIDGE MACHINES
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 OAK RIDGE MACHINES filed Critical OAK RIDGE MACHINES
Priority to US473217A priority Critical patent/US3928969A/en
Priority to GB21114/75A priority patent/GB1510873A/en
Priority to SE7505840A priority patent/SE7505840L/xx
Priority to BR4190/75D priority patent/BR7503277A/pt
Priority to DE19752522977 priority patent/DE2522977A1/de
Priority to CA227,612A priority patent/CA1038262A/en
Priority to JP50062418A priority patent/JPS511878A/ja
Priority to CH669575A priority patent/CH595560A5/xx
Priority to FR7516306A priority patent/FR2272281B1/fr
Application granted granted Critical
Publication of US3928969A publication Critical patent/US3928969A/en
Priority to US05/702,236 priority patent/USRE29620E/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
    • F04D13/043—Units comprising pumps and their driving means the pump being fluid driven the pump wheel carrying the fluid driving means
    • 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

Definitions

  • ABSTRACT A booster for a fluid pressure operated system in which relatively low pressure is used in the system and the booster is designed to be positioned immediately adjacent the fluid operated mechanism so as to elimimate the need for high pressure fittings and components.
  • the booster has a spool which is shiftable in response to pressure build up in the mechanism.
  • the spool acts as a sliding valve to direct fluid flow through a pressure converter such as a turbine or volumetric motor-pump located inside the spool.
  • This invention relates to the field of fluid pressure operated devices, particularlyhydraulically operated tools, rams, motors, etc. It particularly pertains to a device for on the spot boosting of hydraulic pressure so that an entire system does not need to be maintained at a high pressure which is only needed at the point of operation of a fluid pressure operated mechanism.
  • the relatively high pressure can be obtained from a separate source of pressure, by maintaining the entire system at the higher pressure, or by a pressure booster which operates only when the higher pressure is needed.
  • a pressure of 1,500 PSI was formerly considered to be high, but now it is not uncommon to have a pressure of 3,000 PS1 or greater. This can lead to more compact components operating one system with perhaps a smaller fluid reserve, but, it also leads to all of the components being more delicate, therefore more difficult and expensive to manufacture and requiring high quality maintenance.
  • FIG. 1 is a perspective overall view of a hydraulic system showing the booster of this invention at one end of a hydraulic cylinder:
  • FIG. 2 is a schematic representation of the system shown in FIG. 1;
  • FIG. 3 is a sectional view through the booster of the i present invention showing the use of an axial flow turbine and pump as the pressure converter, the converter being located in a shiftable spool which is illustrated to show the fluid flow by-passing the converter;
  • FIG. 4 is a sectional view similar to FIG. 3 but with a shiftable spool in a position where the fluid flow is directed through the pressure converter;
  • FIG; 5 is a sectional view similar to FIG. 3 but illustrating the use of a gear motor-pump as the pressure converter;
  • FIG. 6 is a sectional view similar to FIG. 4 but illustrating the use of a gear motor-pump as the pressure converter;
  • FIG. 7 is a sectional view taken along line 7--7 of FIG. 6; T
  • FIG. 8 is a sectional view taken along line 88 of FIG. 6;
  • FIG. 9 is a perspective view, partly in section, of the booster shown in FIGS.'3 and 4.
  • FIG. 1 illustrates a generally conventional hydraulic cylinder and actuating circuit having a reservoir to hold the fluid, a motor to drive a pump P to force fluid. under pressure into a directional valve where it can be shifted to actuate the piston either inwardly or outwardly in relation to its cylinder.
  • the booster 10 which is the subject of the present invention.
  • FIG. 2 illustrates a setup similar to that of FIG. 1 but where the working cylinder and booster are located at a distance from the reservoir, pump and directional valve, usually by means of flexible hoses.
  • the working cylinder and booster are located at a distance from the reservoir, pump and directional valve, usually by means of flexible hoses.
  • FIG. 3 shows only a portion of the hydraulic cylinder 14, that cylinder having a threaded portion 13 between the body 12 of the booster l0 and the cylinder.
  • the body 12 has inlet port means 16 and outlet port means 18 each with a threaded hose or pipe connection in the outer portion thereof.
  • the body has a bore 20 preferably centrally located with an axially shiftable spool 22 positioned therein.
  • a series of webs in the body define annular flow passages in the body, these webs being axially positioned so as to define different flow paths either through or around the shiftable spool 22 depending upon the axial position of that spool.
  • the spool and bore are machined with a close fitting tolerance between mating surfaces so that a substantially fluid-tight seal can be effected between them.
  • the bore and spool are preferably circular in cross section.
  • the web 24 is axially narrower than the inlet passage opening 26 of the shiftable spool, thus defining a by-pass flow path so that substantially all of the incoming fluid in port means 16 will flow directly into cylinder 14 rather than through spool 22 or into the outlet port means 18.
  • the outlet port means 18 is closed off from fluid flow because shoulder 70 of the spool contacts web 41 of the body.
  • the shifting of the spool 22 is controlled by several factors.
  • a return means At the distal end of the spool is a return means, the present drawings illustrating a spring-dashpot arrangement. It is contemplated that the return means could be in a variety of forms including manual actuation, separate fluid operated means, or electromechanical devices.
  • a spring 28 is held in compression between an adjusting screw 30 and washer 32 and the end of the spool. The spring tends to bias the spool 22 toward the left in FIGS. 3 and 4.
  • the spool 22 will shift to the right as shown in FIG. 4 with the dashpot 34 acting to control the speed of the shifting movement so as to prevent hammering or rapid unstable shifting of the spool.
  • the dashpot 34 is defined by an annular web 39 presenting a cylinder wall 40 which is engaged by a cylinder ring 36 on an extension 33 of the spool, the ring 36 being held in place by a spring retainer ring 38.
  • the opening 42 through which the extension 33 of the spool projects is slightly larger in diameter than that projection for reasons which will be explained in connection with FIG. 4.
  • the amount of force required to shift spool 22 is controlled by several factors: the strength of spring 28, the fit of cylinder ring 36, and a passageway 44 extending through the center of the spool.
  • the size of the return spring can be calculated as follows:
  • the interaction of the blades 58 and vanes 60 is that of an axial flow pump which forces part of the incoming fluid from inlet port 16 therethrough to emerge at considerably higher pressure into cylinder 14'. This supplies the higher pressure required by the cylinder ram when it needs to exert maximum forces.
  • the turbine rotor 56 is supported for rotary movement in sets of bearings, preferably roller bearings 62 and 64. Since the back pressure in cylinder 14 would tend to force rotor 56 toward bearings 64, a small pressure bleedoff passage 66 extends at an angle from passage way 44 so as to place an area 68 located between the rotor and the remainder of the spool at the boosted pressure thus holding the rotor in approximate longitudinal equilibrium.
  • the turbine motor-pump can then act as a pressure converter to change the high volume low pressure incoming flow into a high pressure low volume flow in that portion which is discharged into cylinder 14. Shortly after the spool 22 shifts a considerable portion of the fluid may be diverted into the cylinder 14. However, as the back pressure increases, that volume will be reduced, forcing a greater proportion of the fluid through the motor 50 52. This has the effect of running the turbine faster and thus increasing the pressure output of the pump blades 58 60. If additional pressure is needed it can be obtained by increasing the number of stages in either or both of the motor or pump. A twostage motor and a four-stage pump have been used here only for purposes of illustration. When the back pres-v clearance 74 acts in a manner similar to the orifice 48 to control the speed of the spool shifter, the greater the clearance, the faster the return shift can take place.
  • FIG. 9 better illustrates the construction of spool 22 showing it shifted to the same active position as in FIG. 4, with the flow path through the spool to rotate the turbine motor-pump.
  • the spool has a plurality of openings 94 between webs 95 for the passage of fluid into and out of the spool.
  • the spool is constructed to be opened up along either an axial or longitudinal joint for insertion or servicing of the turbine and its blades or bearings.
  • FIG. 5 is a sectional view similar to FIG. 3 but taken at 90 thereto so that the inlet and outlet port means of the body are not shown but to give a better idea of the remainder of the body 12.
  • FIGS. 5 8 also illustrate an alternative form of pressure converter using a volumetric pump and motor such as a gear motor-pump rather than a turbine. Only parts which are different will be separately described.
  • FIG. 5 includes illustration of an optional cylinder pressure signal 76 which has a passageway 78 to conduct fluid under pressure through a conduit 80 to a pressure gauge, signal device or pressure control valve to remotely control bleeding of dash-pot 34 to shift spool.
  • This pressure signal may be also used with the embodiment of FIGS. 3 4.
  • That portion of the fluid which goes into the pump is then increased in pressure through the action of the pump and then discharged into cylinder 14.
  • the passages of the motor and of the pump are of conventional construction to direct the fluid through the housing 96, around the gears and into the outlet port means 18 in the case of fluid going to the motor or into the mechanism 14 in the case of fluid going to the pump.
  • the volumetric motor-pump is advantageous over the turbine for holding a hydraulic ram in an extended position with a minimum amount of fluid flow to it during the holding operation due to the fact that it is very difficult for any fluid to flow backward through a gear pump or motor.
  • a check valve (not shown) would be used in the inlet port means.
  • another type of volumetric motor-pump such as a piston motor and pump combination could be used. It is to be noted that the check valve while only retaining pressure A at the inlet port, is insuring full boosted pressure holding at the mechanism or motor port.
  • volumetric motors and pumps would be mostly used for lower boosting volume needs andwhen the basic hydraulic system flow must be diverted partially or completely to other tasks while the high pressure is maintained in the mechanism 14.
  • the turbine type motor and pump will be preferable when the full power of the basic system has to be converted to higher pressure to achieve maximum work output by the mechanism under high boosted pressure conditions.
  • Cascades of two or more self-monitored boosters can be connected in series so that the over all system can be used more efficiently in the intermediate pressure range between the low basic system pressure and the maximum boosted pressure. 7
  • the spool could be a different type of sliding means such as a poppet valve I assembly having a frusto-conical seat to effect the sealing between the sliding means or spool and the body.
  • a self-monitored fluid pressure booster .device comprising: a I
  • a body having a bore connectable to a fluid pressure operated mechanism and inlet port means and outlet port means connected to the bore;
  • the device of claim 1 including means to return the sliding means from said second position to said first position.
  • volumetric pump and motor are a gear pump and motor.
  • a self-monitored fluid pressure booster device comprising:
  • a body having a bore with connection means at one end for connection to a fluid pressure operated mechanism, inlet port means and outlet port means in the body axially spaced along and communicating with the bore;
  • a shiftable sliding means in the bore having pressure converter means mounted therein, the pressure converter means having a motor and pump, the sliding means having an outlet passage from the v motor, a discharge passage communicating the pump to said connection means and an inlet passage conne'cted to the motor and the pump;
  • said sliding means being mounted for axial shifting along the bore from a first inactive position in which the inlet portmeans is connected for fluid to flow directly to the mechanism and the outlet passages are blocked to a second active position in which the inlet port means is aligned with the inlet passage and the outlet port meansis aligned with the outlet passage so that fluid pressure in the inlet port means will cause fluid to flow through the inlet passage to both the motor and the pump, the motor driving the pump to create a zone of boosted pressure in.the discharge passage, the shifting of the sliding means being a response to the pressure in said zone.
  • the device of claim 9 including means to return the sliding means from said second position to said first position.
  • volumetric type pump and motor is a gear pump and motor.
  • a self-monitored fluid pressure booster device comprising:
  • a body having a circular bore with one end being open to present connection means to attach the body to afluid pressure operated mechanism, an inlet port and an outlet port in the body axially spaced along and communicating with the bore;
  • a cylindrical sliding means in the bore mounted for axial shifting, a pressure converter in the sliding means having a fluid operated motor directly connected to a fluid pump, an outlet passage from the motor, a discharge passage from the pump to the area of the connection means and an inlet passage connected to both the motor and the pump;
  • the inlet and outlet ports in the body being positioned in relation to said shoulders so that in a first axially shifted position the first shoulder permits passage of fluid directly from the inlet port to the area of the connection means and the second shoulder blocks off the outlet passage and in a second axially shifted position the first shoulder blocks off direct fluid flow from the inlet port to the area of the connection means, directing the fluid flow from the inlet port to the inlet passage of the sliding means and the second shoulder is positioned to permit fluid flow from the outlet passage of the sliding means to the outlet port of the body;
  • biasing means in said dashpot tending to return the sliding means to said first position upon a decrease in pressure in the area of said connection means.
  • volumetric type pump and motor is a gear pump and motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Motors (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
US473217A 1974-05-24 1974-05-24 Self-monitored fluid pressure booster system Expired - Lifetime US3928969A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
US473217A US3928969A (en) 1974-05-24 1974-05-24 Self-monitored fluid pressure booster system
GB21114/75A GB1510873A (en) 1974-05-24 1975-05-19 Selt-monitored fluid pressure booster system
SE7505840A SE7505840L (sv) 1974-05-24 1975-05-22 Tryckforsterkare.
DE19752522977 DE2522977A1 (de) 1974-05-24 1975-05-23 Fluiddruckverstaerker
BR4190/75D BR7503277A (pt) 1974-05-24 1975-05-23 Aperfeicoamento em dispositivo reforcador de pressao de fluido autocontrolado
CA227,612A CA1038262A (en) 1974-05-24 1975-05-23 Self-monitored fluid pressure booster system
JP50062418A JPS511878A (US20030199744A1-20031023-C00003.png) 1974-05-24 1975-05-24
CH669575A CH595560A5 (US20030199744A1-20031023-C00003.png) 1974-05-24 1975-05-26
FR7516306A FR2272281B1 (US20030199744A1-20031023-C00003.png) 1974-05-24 1975-05-26
US05/702,236 USRE29620E (en) 1974-05-24 1976-07-02 Self-monitored fluid pressure booster system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US473217A US3928969A (en) 1974-05-24 1974-05-24 Self-monitored fluid pressure booster system

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/702,236 Reissue USRE29620E (en) 1974-05-24 1976-07-02 Self-monitored fluid pressure booster system

Publications (1)

Publication Number Publication Date
US3928969A true US3928969A (en) 1975-12-30

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ID=23878656

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US473217A Expired - Lifetime US3928969A (en) 1974-05-24 1974-05-24 Self-monitored fluid pressure booster system
US05/702,236 Expired - Lifetime USRE29620E (en) 1974-05-24 1976-07-02 Self-monitored fluid pressure booster system

Family Applications After (1)

Application Number Title Priority Date Filing Date
US05/702,236 Expired - Lifetime USRE29620E (en) 1974-05-24 1976-07-02 Self-monitored fluid pressure booster system

Country Status (9)

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US (2) US3928969A (US20030199744A1-20031023-C00003.png)
JP (1) JPS511878A (US20030199744A1-20031023-C00003.png)
BR (1) BR7503277A (US20030199744A1-20031023-C00003.png)
CA (1) CA1038262A (US20030199744A1-20031023-C00003.png)
CH (1) CH595560A5 (US20030199744A1-20031023-C00003.png)
DE (1) DE2522977A1 (US20030199744A1-20031023-C00003.png)
FR (1) FR2272281B1 (US20030199744A1-20031023-C00003.png)
GB (1) GB1510873A (US20030199744A1-20031023-C00003.png)
SE (1) SE7505840L (US20030199744A1-20031023-C00003.png)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4043127A (en) * 1975-07-02 1977-08-23 Kubik Philip A Reservoir housing
US4099905A (en) * 1977-04-29 1978-07-11 Cincinnati Milacron Inc. Injection molding machine base
US4193733A (en) * 1978-05-17 1980-03-18 Harnischfeger Corporation Hydraulic excavator machine having self-contained electrohydraulic power units
US4467604A (en) * 1979-12-24 1984-08-28 Linde Aktiengesellschaft Hydrostatic drive system for an excavator
DE19839783B4 (de) * 1997-09-04 2006-04-06 Kubota Corp. Steuerventilmechanismus für ein Arbeitsfahrzeug mit drehbarem Aufbau
US20110173966A1 (en) * 2008-06-27 2011-07-21 Harald Klahm Hydraulic agregate
CN104481967A (zh) * 2014-12-22 2015-04-01 丹东华信测控技术有限公司 一种电液回转器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8303277B2 (en) * 2002-11-21 2012-11-06 International Dispensing Corporation Blending pump assembly
US7131826B1 (en) * 2002-11-21 2006-11-07 International Dispensing Corporation Blending pump assembly

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2802452A (en) * 1953-10-20 1957-08-13 Bosch Arma Corp Hydraulic starter
US2845868A (en) * 1955-01-12 1958-08-05 Borg Warner Gear pump
US3386340A (en) * 1965-11-24 1968-06-04 Elisworth C. Engle Fluid power drive unit having rotary and reciprocatory movement

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1839144A (en) * 1928-06-01 1931-12-29 Flagg Charles Noel Float operated control valve
US2388877A (en) * 1941-12-01 1945-11-13 Eugene H Souter Squeeze riveter
US3385217A (en) * 1966-02-21 1968-05-28 Marcus J. Bles Hydraulic pressure booster
DE1550316B2 (de) * 1966-10-25 1971-05-27 Herion Werke KG, 7012 Fellbach Druckmittelbetaetigtes membranventil mit einer durch einen stift gereinigten drosselstelle
DE2001387A1 (de) * 1970-01-14 1971-08-26 Volkswagenwerk Ag Zylinderanordnung zur Krafterzeugung mit einem Arbeits- und einem UEbersetzungszylinder

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2802452A (en) * 1953-10-20 1957-08-13 Bosch Arma Corp Hydraulic starter
US2845868A (en) * 1955-01-12 1958-08-05 Borg Warner Gear pump
US3386340A (en) * 1965-11-24 1968-06-04 Elisworth C. Engle Fluid power drive unit having rotary and reciprocatory movement

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4043127A (en) * 1975-07-02 1977-08-23 Kubik Philip A Reservoir housing
US4099905A (en) * 1977-04-29 1978-07-11 Cincinnati Milacron Inc. Injection molding machine base
US4193733A (en) * 1978-05-17 1980-03-18 Harnischfeger Corporation Hydraulic excavator machine having self-contained electrohydraulic power units
US4467604A (en) * 1979-12-24 1984-08-28 Linde Aktiengesellschaft Hydrostatic drive system for an excavator
DE19839783B4 (de) * 1997-09-04 2006-04-06 Kubota Corp. Steuerventilmechanismus für ein Arbeitsfahrzeug mit drehbarem Aufbau
US20110173966A1 (en) * 2008-06-27 2011-07-21 Harald Klahm Hydraulic agregate
US9080561B2 (en) * 2008-06-27 2015-07-14 Hydac Fluidtechnik Gmbh Hydraulic aggregate
CN104481967A (zh) * 2014-12-22 2015-04-01 丹东华信测控技术有限公司 一种电液回转器

Also Published As

Publication number Publication date
CA1038262A (en) 1978-09-12
SE7505840L (sv) 1975-11-25
USRE29620E (en) 1978-05-02
JPS511878A (US20030199744A1-20031023-C00003.png) 1976-01-09
DE2522977A1 (de) 1975-11-27
CH595560A5 (US20030199744A1-20031023-C00003.png) 1978-02-15
GB1510873A (en) 1978-05-17
FR2272281A1 (US20030199744A1-20031023-C00003.png) 1975-12-19
BR7503277A (pt) 1976-04-27
FR2272281B1 (US20030199744A1-20031023-C00003.png) 1979-03-16

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