US3831496A - Pressure responsive control body arrangement - Google Patents

Pressure responsive control body arrangement Download PDF

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Publication number
US3831496A
US3831496A US00239551A US23955172A US3831496A US 3831496 A US3831496 A US 3831496A US 00239551 A US00239551 A US 00239551A US 23955172 A US23955172 A US 23955172A US 3831496 A US3831496 A US 3831496A
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United States
Prior art keywords
control
rotor
control body
fluid
pressure chamber
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Expired - Lifetime
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US00239551A
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English (en)
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K Eickmann
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Individual
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Individual
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Priority to US321853A priority Critical patent/US3889577A/en
Priority to US05/487,271 priority patent/US3960060A/en
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Publication of US3831496A publication Critical patent/US3831496A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like

Definitions

  • a pressure responsive control body arrangement is provided in a fluid handling device thereby, that axially of one end of the fluid handling rotor which contains the fluid intaking and expelling working chambers a pressure responsive fluid flow control body is adapted against the rotary control face of the rotor to seal with its stationary control face along said rotary control face while said control body is partially contained in a fluid containing pressure chamber; axially V moveable therein in a limited extend, forming sepaand sealing therein one portion of the fluid containing chamber from another portion thereof, while in order to locate the pressure centre of said eccentric portion of said control body at the same position.
  • the eccentric shoulder of said control body partially extends radially over the outer diameter of said control faces.
  • This location of the eccentric shoulder of the invention provides, a smooth running of the control faces along each other whereby tilting or sticking between them is effectivley prevented, so, that the control mirror between the rotary and the stationary control faces of the device operate at high efficiency also at high pressures in fluid and high relative velocities between them.
  • the present invention relates to a pressure responsive control body atrangement in a fluid handling device, such as a hydraulic or pneumatic pump, compressor, motor, engine or transmission or the like, having working chambers whereto displacement members are associated for taking fluid into and out of said working chambers.
  • a fluid handling device such as a hydraulic or pneumatic pump, compressor, motor, engine or transmission or the like
  • Rotary fluid handling devices of this type are well known and have been proven reliable.
  • a typical apparatus of this kind is disclosed in my U.S. Pat. No. 3,561 ,328.
  • the said known fluid handling device how ever and the related devices have the disadventage that the structure is not compact enough, that the production costs and times are still too expensive and that the efficiency should still be improved.
  • the device of my above mentioned patent has further the disadvantage that for higher pressure or relative velocities between the stationary and rotary control faces the application of the opposition chamber was nevessary in order to counteract to locally too strong pressure forces, which otherwise pressed the rotary and stationary control face of the locally too strongly together.
  • Another object of the invention is, to spare the heretofore used opposition chamber on a shoulder of the control body and also to spare the communications and control arrangements associated to said opposition chamber of said control body.
  • a further object of the invention is, to acheave the elimination of the expensive opposition chamber and its associated members without reducing the reliability of the pressure responsive control body of the fluid handling device.
  • the diameter of the shoulder of the control body would be narrowed together with b. the pressure centre of the fluid pressure chamber portion, whereinto the control body shoulder extends, would be moved more radially away from the centre line of the rotor of the device in order to get the same distance from the axis of the machine as the pressure centre in the fluid between the stationary and rotary control face has. It has further been found in accordance with this invention, that only one single seal would be needed in association with the fluid containing pressure chamber and the control body with an eccentric portion, if the eccentric portion would be correctly dimensioned andlocated in a one directional delivery or intaking fluid handling device.
  • the shoulder of the control body is of cylindrical configuration, but eccentrically distanced from the axis of the rotor in such extend, that even at the de sired small, but necessary diameter of the eccentric shoulder of the controlbody a part of said eccentric shoulder extends radially at one location beyond the outer diameter of the stationary or rotary control face of the fluid handling device; or, that 2nd, in a one directionl flow device the control body has only one single centric portion and only one single eccentric portion, why one portion thereof may be unsealed; or that 3rd, the member containing the fluid containing pressure chambers and partially containing said control body is assembled by two different portions, so that the eccentric shoulder of said control body may be contained between both portions; or that 4th, the end portion of the control body is reduced to a minimal diameter in order to make the radial extension of the eccentric shoulder over the outer diameter of the control face possible; or that 5th, the rotor passages are inclined from the bottoms of the working chambers radially inwanrdly in order to port at the
  • the fluid containing pressure chamber is located in a single body or located in a body assembled by a plurality of parts;
  • That the fluid containing pressure chamber has only one sealed chamber portion or two sealed chamber portions;
  • control body has only one eccentric and one centric portion or it has one eccentric and two centric portions;
  • FIG. 1 is a longitudinal view through an embodiment of the invention.
  • FIG. 2 is a longitudinal sectional view through a portion of a fluid handling device containing another embodiment of the invention.
  • a rotor l is rotatably borne in bearings and axially at one end of said rotor supported on a thrust bearing 37.
  • the rotor contains the fluid handling working chambers, for example 2 and 3 or a plurality thereof and displacement members 4 are associated to the working chambers 2 or 3 in order to guide the expan' sion and contraction of the volume of the working chambers.
  • Rotor passages 12 and 13 extend from the respective working chambers to an end of the rotor l and therethrough to form rotor ports in an axial end of the fluid handling rotor l for leading fluid into or out of said working chambers 2 or 3 in the rotor of the fluid handling device.
  • a hosing portion or cover portion 14 of the device a fluid containing pressure chamber 8,9,21,22 is provided and a control body, also called thrust member or control chuck 7 is partially located in said fluid containing pressure chamber and forms a stationary controlface face 20 on the end of said controlbody adjacent to said rotor for sliding and sealing along the rotary control face 19 on the adjacent axial end of the rotor l.
  • the fluid acting in the fluid containing pressure chambers 8,9,2] or 22 are pressing the control body 7 axialwardly against the endface 19 of the fluid handling rotor 1, so, that no leakage or only small leakage escapes through the control clearance, which is formed between the two control faces, the stationary control face 20 of control body 7 and the rotary control face 19 of rotor 1.
  • the control body 7 has at least one centric portion 7 or 7 and 15 and at least one excentric portion 31. Fluid flows from port 10 through passage 5 and port 5 (control port 5 and through rotor passages 12 or 13 into the respective fluid handling working chambers 2 or 3 and out of them through the respective rotor passages 12 or 13 and control port 6 and passage 6 to and out out of port 11 or vice versa.
  • the counter balancing opposition chamber was applied onto the control body for acting contrary in direction to the fluid forces which acted onto the control body in the direction against the rotor.
  • the latter was necessary, because the end portion of the control body of the said U.S. Pat. No. 3,561,328 had a bid diameter axial end portion on the backwards end of the control body. That made a large diameter of the excentric shoulder of the control body necessary, while on the other hand the big diameter of the end portion of the control bpdy prevented a larger excentric location of the excentric shoulder of the control body. Because the diameter of an end portion on the backward end of the control body limits the eccentric location of the eccentric portion of the control body.
  • This feature of thne invention makes it possible, to eliminate the heretofore used counter balancing opposition chamber, because; only if the eccentric portion extends radially partially beyond the outer diameter of the control face is it possible to place the pressure centre of the fluid containing pressure chamber portion and of the eccetric shoulder 31 of control body 7 exactly into the same position relatively to the rotor axis, which the pressure centre of the fluid in thne fluidfilm between the stationary and rotary controlfacees 19 and has. Only if said both pressure centres have the same axis parallel to the axis of the rotor is an even pressing of the control body against the rotor 1 possible without local over pressures and under pressures.
  • the associated portion in thne fluid film is to be considered to be the high pressure aquivalent area within said control clearance between said stationary and rotary control faces 19 and 20.
  • This aquivalent area consists actually of a high pressure area plus an area of pressure drop, which i mean has a lesser fluid pressure, but beeing calculated as a lesser area of high pressure, called the high pressure equivalent area.
  • the eccentric shoulder extended also beyond the outer diameter of the control face, but the crossectional area through the eccentric shoulder was many percent larger than thne associated pressure aquivalent area in the control clearance, whereby the application of the opposition chamber became necessary.
  • the opposition chamber is spared, because the excentric extension of the eccentric shoulder 31 oever the diameter of control face 19,20 is combined with the reduction of the crossectional area through the eccentric shoulder 31 to a few percent over the area of the pressure aquivalent area in the control clearance 19-20. And, thereby, the opposition chamber is spared by this invention.
  • FIG. 2 The most simplest embodiment of the invention is demonstrated in FIG. 2. From port 24 flows fluid through the fluid containing suction chamber or intake chamber 22 and through passage and control port 6 and through the control clerance 19 20 and through the respective rotor passages 13 or 12 into the respective working chambers in rotor l and out thereof through again respective rotor passages 12 or 13 and the control clearance 19 20 into and through control port 5 and through passage 5 and through pressure chamber 21 into and through exit port 23 of the fluid separated from each other and sealed against each other by the seat 16, which is preferred to be a cylindrical configuration. This cylindrical configuration how ever has an axis, which is eccentric relatively to the centric axis of rotor 1 and of the centric portion 7 of control body 7.
  • the fluid pressure chamber 22 may further be sealed by the seat 17.
  • This seat is also of prefferedly cylindrical configuration. However this cylindrical configuration is centred around the centrical axis of control body or control chuck or thrust member 7. Saif centrical axis is equal to the axis of the revolving rotor l of the fluid handling device.
  • high pressure in fluid can either be present in pressure chamber 21 or in pressure chamber 22 and in each case the pressure in fluid in the respective fluid containing pressure chamber portion 21 or 22 will presse the control body 7 in axial direction against the end 19 or the rotor l of the device, so, that both control faces 19 and 20 are pressed together and form together the self sealing control clearance 19 20 between the stationary control face 20 and the rotary control face 19.
  • the control body 7 is axxially within a limited extend moveable within the pressure chambers 21 22.
  • Thecrossectional area through the eccentric portion or shoulder 31 of the control body should be, according to the invention, restricted to be only a few percent, f.e. 4 to 6 percent, larger than the crossectional area through the respective high pressure aquivalent area in the respective portion between the control faces 19 and 20 of the device.
  • the eccentricity of the eccentric portion or shoulder 31 should be of such dimension, that the pressure centres of the shoulder 31 and of the respective portion of the control means between faces 19 and 20 are in the same axis, eccentric to, but also parallel to the axis of the rotor 1 of the device.
  • the device operates effectively also at high and very high pressures and relative velocities between the control faces 19 and 20.
  • the eccentric shoulder 31 of control chuck 7 will exxtend partially beyomd the outer diameter of control face 20, while no opposition chamber will be present at the opposite end of the eccentric shoulder 31.
  • the portion 31 in seat 16 is the eccentric shoulder 31 of the control body or control chuck, 7. Since it partially extends radially beyond the outer diameter of the control face of the controlbody or control chuck 7; it is necessary. if the seat 17 shall also seal, as it must, if the device is of the flow reversing type, to divide the housing portion 14 along the face 18 or a face parallel to face 18, in order to make the machining of the housing portion 14 with its seat 16 and the insertion of the control body 7 thereinto possible. After such divisoon and insertion of the control body 7 into its seats, the housing portion 18 has to be assembled again and a seal hs to take place along the face 18.
  • the control, body or control chuck 7 remains movebale in axial direction within housing portion 14 and sealed within seats 15,16 and 17, if built in accordance with the rooles of this invention.
  • a combination comprising a housing; a rotor mounted in said housing and having a first control face at one axial end thereof, a plurality of working chambers and first passages extending between said working chambers and said first control face, said housing having inlet and outlet ports for admission and evacuation of fluid and pressure chamber means communicating with said ports; and a control body axially movably received in said pressure chamber means and having a second control face adjacent to and defining with said first control face a narrow control clearance, said control body being urged toward said rotor by fluid in said pressure chamber means and including at least one larger-diameter first cylindrical portion coaxial with said rotor and at least one smaller-diameter second cylindrical portion which is eccentric relative to said rotor and extends in part radially beyond at least one of said control faces, said control body further having second passages alternatingly connecting said first passages with said inlet and outlet ports when said rotor rotates relative to said housing.
  • said housing comprises a plurality of parts assembled with and connected to each other upon insertion of said control body into said pressure chamber means.
  • said pressure chamber means includes a high-pressure chamber for said second cylindrical portion and a lowpressure chamber for said first cylindrical portion of said control body.
  • each of said working chambers has a bottom portion and said first passages extend from the bottom portions of the respective working chambers and substantially radially inwardly of said rotor so that the distance between said first passages and the axis of said rotor in the region of said first control face is less than the distance between said bottom portions and the axis of said rotor.
  • a combination comprising a housing; a rotor mounted in said housing and having a first control face at one axial end thereof, a plurality of working chambers and first passages extending between said working chambers and said first control face, said housing having inlet and outlet ports for admission and evacuation of fluid and pressure chamber means communicating with said ports; and a control body axially movably received in said pressure chamber means and having a second control face adjacent to and defining with said first control face a narrow control clearance, said control body being urged toward said rotor by fluid in said pressure chamber means and including at least one larger-diameter first cylindrical portion coaxial with said rotor, at least one smaller-diameter second cylindrical portion which is eccentric relative to said rotor and extends in part radially beyond at least one of said control faces, and a third cylindrical portion which is coaxial with said first cylindrical portion and has a diameter which is a fraction of the diameter of said first cylindrical portion, said control body further having second passages alternatingly connecting said first passage
  • a combination comprising a housing; a rotor mounted in said housing and having a first control face at an axial end thereof, a plurality of working chambers and first passages extending between said working chambers and said first control face, said housing having inlet and outlet ports for admission and evacuation of fluid and pressure chamber means communicating with said ports; and a control body axially movably received in said pressure chamber means and having asecond control face adjacent to and defining with said first control face a narrow control clearance, said control body being urged toward said rotor by fluid in said pressure chamber means and including at least one larger-diameter first cylindrical portion coaxial with said rotor, at least one smaller-diameter second cylindrical portion which is eccentric relative to said rotor, and a third cylindrical portion which is coaxial with said first cylindrical portion and has a diameter which is a fraction of the diameter of said first cylindrical portion, said control body further having second passages altematingly connecting said first passages with said inlet and outlet ports when said rotor rotates

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
US00239551A 1971-04-07 1972-03-30 Pressure responsive control body arrangement Expired - Lifetime US3831496A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US321853A US3889577A (en) 1972-01-05 1973-01-08 Pressure-responsive control body for use in fluid handling devices
US05/487,271 US3960060A (en) 1971-04-07 1974-07-10 Pressure responsive control body arrangement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT298771A AT326484B (de) 1971-04-07 1971-04-07 Stromungsmaschine mit axialem einlass und auslass-insbesondere radialkolben-pumpe oder-motor

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US05/487,271 Continuation-In-Part US3960060A (en) 1971-04-07 1974-07-10 Pressure responsive control body arrangement

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DE (1) DE2214771A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3960060A (en) * 1971-04-07 1976-06-01 Karl Eickmann Pressure responsive control body arrangement
US4557347A (en) * 1981-07-14 1985-12-10 Karl Eickmann Fluid pumps, fluid motors and devices, wherein they are applied

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2528768C2 (de) * 1974-07-10 1986-03-06 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Steuervorrichtung für eine pneumatische oder hydrostatische Maschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2525498A (en) * 1944-08-15 1950-10-10 Vickers Armstrongs Ltd Radial pump or hydraulic motor
US2809594A (en) * 1953-05-11 1957-10-15 New York Air Brake Co Fluid pressure mechanism
US2861552A (en) * 1956-09-28 1958-11-25 Ford Motor Co Power transmission arrangements for hydraulically propelled vehicles
US3092036A (en) * 1960-05-18 1963-06-04 Ford Motor Co Hydraulic pumps or motors
US3457808A (en) * 1965-09-06 1969-07-29 Karl Eickmann Hydrostatic-mechanical transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2525498A (en) * 1944-08-15 1950-10-10 Vickers Armstrongs Ltd Radial pump or hydraulic motor
US2809594A (en) * 1953-05-11 1957-10-15 New York Air Brake Co Fluid pressure mechanism
US2861552A (en) * 1956-09-28 1958-11-25 Ford Motor Co Power transmission arrangements for hydraulically propelled vehicles
US3092036A (en) * 1960-05-18 1963-06-04 Ford Motor Co Hydraulic pumps or motors
US3457808A (en) * 1965-09-06 1969-07-29 Karl Eickmann Hydrostatic-mechanical transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
N. A. Shute & D. E. Trunbull; The Thrust Balancing of Axial Piston Machines, May 1963 & June 1963, published by British Hydromechanics, Research Association. *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3960060A (en) * 1971-04-07 1976-06-01 Karl Eickmann Pressure responsive control body arrangement
US4557347A (en) * 1981-07-14 1985-12-10 Karl Eickmann Fluid pumps, fluid motors and devices, wherein they are applied

Also Published As

Publication number Publication date
AT326484B (de) 1975-12-10
ATA298771A (de) 1975-02-15
DE2214771A1 (de) 1972-11-09

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