US3898021A - Rotary expansible chamber device with variable eccentricity - Google Patents

Rotary expansible chamber device with variable eccentricity Download PDF

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Publication number
US3898021A
US3898021A US448230A US44823074A US3898021A US 3898021 A US3898021 A US 3898021A US 448230 A US448230 A US 448230A US 44823074 A US44823074 A US 44823074A US 3898021 A US3898021 A US 3898021A
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United States
Prior art keywords
rotor
annulus
stator
blocks
rotation
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Expired - Lifetime
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US448230A
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English (en)
Inventor
Edouard Robe Barneoud-Arnoulet
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BARNEOUD ARNOULET EDOUARD ROBE
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BARNEOUD ARNOULET EDOUARD ROBE
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/20—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the form of the inner or outer contour of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type

Definitions

  • ABSTRACT A hydraulic transmission or speed-change device or the like, of the type comprising a stator, an input rotor to which an input shaft is connected, and an output rotor to which an output shaft is connected, with expansible chambers between adjacent pairs of these members, is characterized by a flexible annulus fixed against rotation relative to one of the members but radially deformable relative thereto. Deformation of the annulus is effected by means of fluid pressure jacks that actuate wedges in a direction parallel to the common axis of rotation. At least some of the relatively movable portions of at least some of the expansible chambers slide against this annulus with a stroke that varies as the deformation of the annulus.
  • the present invention relates to rotary expansible chamber devices of the type in which relatively rotatable members have nonconcentric guide surfaces for causing cyclic expansion and contractionof chambers into which the working fluid is drawn and from which the working fluid is expelled.
  • Devices of this type are well known as speed-change mechanisms or hydraulic transmissions or the like.
  • One such mechanism to which the present invention is applicable is disclosed in my French Pat. No. 1,073,662, to which reference will be had for further disclosure of the environment of my invention, thereby to avoid the need for such further disclosure in the present application.
  • Devices of the type of the present invention comprise generally a stator, a rotor connected to an input and another rotor connected to an output. Expansible chambers are formed between these elements, the elements having nonconcentric surfaces thereon such that upon relative rotation of the elements, the chambers will expand or contract thereby to admit and expel] the working fluid. It is of course well known in such devices that r the greater is the eccentricity or nonconcentricity of the surfaces, the greater will be the volume of fluid flow, with corresponding changes in the speeds and power ratios that are obtainable.
  • the present invention has as its object the provision of such a device, in which the displacement of the working fluid is readily regulable.
  • Another object of the present invention is the provision of such a device which will be relatively simple and inexpensive to manufacture, easy to operate, maintain and repair, compact in configuration, and rugged and durable in use.
  • the'objects of the invention are achieved by providing a deformable annulus connected to but radially movable relative to one of the three principal elements (stator, input rotor, output rotor), thereby to provide in effect a working surface on that associated element which is of variable curvature.
  • Wedge means are provided, movable parallel to the common axis of rotation of the rotors to deform the annulus. The deformation is symmetrical relative to the axis of rotation and so the forces remain in balance.
  • the deformable annulus is provided with blocks that slide in corresponding recesses in the number with which the annulus is associated.
  • Wedge means are provided for moving the blocks in and out of their associated recesses in a manner that is symmetrical with respect to the axis of rotation, the wedge means moving in a direction parallel to that axis under the influence of operating means such as jacks such as fluid cylinders.
  • Actuation of the jacks to a controlled degree accordingly alters the curvature of the deformable annulus to a corresponding degree, thereby to regulate the stroke of the expansible chambers and correspondingly to regulate the pressure and speed relationships of the device.
  • the three principal elements overlap each other axially, the stator being outermost and the two rotors being innermost.
  • the inner surface of the stator has inwardly opening recesses in which sliding blocks are disposed for radial movement, these blocks sliding on the outer surface of the flexible annulus which has blocks secured to its inner surface that are received in recesses in the outer surface of the outer of th e two rotors, the two rotors having further recess and slidingblock assemblies between themselves.
  • the invention may for example be embodied in a motor having a volumetric pump integral with a rotatable portion of the motor, thereby to constitute a speed-change mechanism.
  • FIG. 1 is a schematic axial view of a device according to the present invention.
  • FIG. 2 shows an enlarged cross section of one of the slide blocks between the flexible annulus and the surrounding stator
  • FIG. 3 is an enlarged cross-sectional view in the plane of the axis of rotation, showing one of the wedge devices to vary the shape of the flexible. annulus.
  • the device of the present invention comprises a stator 9 or outer ring in the form of an exterior cage, in which are concentrically disposed an input rotor 3 and an output rotor 13, which may be fixed either directly or through suitable speed-change devices (not shown) to input and output shafts (not shown) respectively.
  • Two wedges 4 are provided in recesses in diametrically opposed blocks 2.
  • Wedges 6 slide on wedges 4 and are actuated by stationary fluid pressure jacks 7 that move members 8 parallel to the axis of rotation.
  • Members 8, in turn, are received in an annular ring 8' to which the wedges 6 are secured, the ring 8" thus rotating with rotor 3.
  • the degree to which jacks 7 are actuated by a source of fluid under pressure thus regulates the eccentricity of annulus 1 by moving the blocks 2 in or out of their recesses, the resilience of the annulus 1 maintaining wedges 4 and 6 in Contact with each other.
  • Stator 9 has recesses 9' which are of cylindrical cross section as best seen in FIG. 2 and that have rounded edges. Segments 5 are disposed in recesses 9' and are urged slidably against annulus l by springs 10 or other conventional devices such as magnets. Only a relatively small surface area of segments 5 is applied against annulus 1 thanks to communication opening 5' through segments 5 which balances the forces and reduces friction.
  • the blocks 2 and the segments 5 near these blocks delimit between the rotor 3 and the stator 9 four compartments.
  • recesses or holes 1 through annulus 1 permit the circulation of fluid such as hydraulic fluid.
  • Canals 11 and 11 bring the fluid into two opposed compartments and canals l2 and 12' evacuate the fluid from the other two compartments.
  • Lateral seals (not shown) are carried by stator 9 on either side of the assembly and thus assure lateral fluid tightness.
  • the rotor 13 is concentric within rotor 3 and may with the rotor 13 comprise a pump.
  • the pump has segments 14 of the same type as the segments 5.
  • the pump has an output flow proportional to the relative rotation of the tworotors.
  • An oil inlet (not shown) through the shaft of rotor 13 supplies to the pump sufficient fluid to make up losses.
  • the output rotor 3 behaves as a rotatable piston and modifies the speed and force exerted by the input rotor 13 according to the eccentricity of the annulus l, which in turn is regulated by the FIG. 3 mechanism.
  • the eccentricity that is, the deformation from circular configuration
  • the fluid flow is also at the maximum and the'speed is at a minimum.
  • the annulus l is circular or nearly circular, then there is no substantial output flow from the pump and the rotor 3 turns at substantially the same speed as the rotor 13, except of course for a small slippage due to losses.
  • the jack 7 can also unlatch the stator 9 at a predetermined point, so that the latter can turn freely and thus reduce slippage.
  • Means are of course provided for controlling the jack 7 to modify the shape of annulus 1.
  • these might of course be means responsive to the speed of the input shaft which would be detected and would control the outflow of an auxiliary pump driven by the input shaft.
  • the detector would act on a distributor which would charge or discharge the jack 7.
  • Other such systems can be devised.
  • a fluid transmission comprising an annular stator, a first annular rotor within said stator, a second rotor within said first rotor, a flexible annulus surrounding said first roto between said stator and said first rotor,
  • rotor a plurality of expansible chambers, means defining between said rotors spaced chambers that vary in volume upon relative rotation of said rotors.
  • said spaced chambers communicating through passageways through said first rotor with said expansible chambers, blocks secured to said annulus and slidable radially in recesses in said first rotor thereby to fix said annulus against rotation relative to said first rotor, and means for deforming said annulus from circular form thereby to regulate the expansion and contraction of said expansible chambers upon rotation of said first rotor, said deforming means comprising means bearing against said blocks to impart to said blocks a non-circular path upon rotation of said first rotor.
  • bearing means comprising fluid pressure jacks that act in a direction parallel to the axis of the rotor to urge wedges against said blocks.
  • each of said segments having spaced lips thereon that bear slidably against said annulus.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US448230A 1973-03-05 1974-03-05 Rotary expansible chamber device with variable eccentricity Expired - Lifetime US3898021A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7307666A FR2221032A5 (enExample) 1973-03-05 1973-03-05

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US3898021A true US3898021A (en) 1975-08-05

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US (1) US3898021A (enExample)
DE (1) DE2408074A1 (enExample)
FR (1) FR2221032A5 (enExample)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4851723A (en) * 1988-08-01 1989-07-25 Westinghouse Electric Corp. Coolant pump system for variable speed generators
WO1996041067A1 (en) * 1995-06-07 1996-12-19 Folsom Technologies, Inc. Infinitely variable vane-type hydraulic machine
US5839889A (en) * 1991-01-14 1998-11-24 Folsom Technologies, Inc. Infinitely variable vane-type hydraulic machine
US5956953A (en) * 1997-02-08 1999-09-28 Folsom; Lawrence R. Concentric radial piston transmission with flexible cam ring
US6022201A (en) * 1996-05-14 2000-02-08 Kasmer Hydristor Corporation Hydraulic vane pump with flexible band control
US6200114B1 (en) * 1996-11-08 2001-03-13 Hobourn Automotive Limited Variable flow pump
US20050036897A1 (en) * 2003-08-11 2005-02-17 Kasmer Thomas E. Rotary vane pump seal
US9133830B2 (en) 2008-10-31 2015-09-15 Eaton Corporation Fluid device with flexible ring

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368223A (en) * 1940-11-23 1945-01-30 Manly Corp Fluid pressure device
US2842064A (en) * 1954-05-24 1958-07-08 Gunnar A Wahlmark Hydraulic pressure unit

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368223A (en) * 1940-11-23 1945-01-30 Manly Corp Fluid pressure device
US2842064A (en) * 1954-05-24 1958-07-08 Gunnar A Wahlmark Hydraulic pressure unit

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4851723A (en) * 1988-08-01 1989-07-25 Westinghouse Electric Corp. Coolant pump system for variable speed generators
US5839889A (en) * 1991-01-14 1998-11-24 Folsom Technologies, Inc. Infinitely variable vane-type hydraulic machine
WO1996041067A1 (en) * 1995-06-07 1996-12-19 Folsom Technologies, Inc. Infinitely variable vane-type hydraulic machine
US6022201A (en) * 1996-05-14 2000-02-08 Kasmer Hydristor Corporation Hydraulic vane pump with flexible band control
US6200114B1 (en) * 1996-11-08 2001-03-13 Hobourn Automotive Limited Variable flow pump
US5956953A (en) * 1997-02-08 1999-09-28 Folsom; Lawrence R. Concentric radial piston transmission with flexible cam ring
US20050036897A1 (en) * 2003-08-11 2005-02-17 Kasmer Thomas E. Rotary vane pump seal
US7484944B2 (en) 2003-08-11 2009-02-03 Kasmer Thomas E Rotary vane pump seal
US9133830B2 (en) 2008-10-31 2015-09-15 Eaton Corporation Fluid device with flexible ring

Also Published As

Publication number Publication date
DE2408074A1 (de) 1974-09-26
FR2221032A5 (enExample) 1974-10-04

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