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US1961592A - Variable capacity pump or motor - Google Patents

Variable capacity pump or motor Download PDF

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Publication number
US1961592A
US1961592A US333452A US33345229A US1961592A US 1961592 A US1961592 A US 1961592A US 333452 A US333452 A US 333452A US 33345229 A US33345229 A US 33345229A US 1961592 A US1961592 A US 1961592A
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US
United States
Prior art keywords
shaft
motor
fluid
pump
ring
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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
US333452A
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English (en)
Inventor
Muller Wolfgang Carl
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Individual
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Application filed by Individual filed Critical Individual
Priority to US333452A priority Critical patent/US1961592A/en
Priority to DEM113336D priority patent/DE547594C/de
Priority to GB335/30A priority patent/GB334476A/en
Priority to FR687901D priority patent/FR687901A/fr
Application granted granted Critical
Publication of US1961592A publication Critical patent/US1961592A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F16H39/02—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motors at a distance from liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
    • F01C1/332—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F01C1/336—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/38—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member
    • 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
    • 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
    • F04C14/22—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 eccentricity between cooperating members
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • 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
    • F16H39/22—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 with liquid chambers shaped as bodies of revolution concentric with the main axis of the gearing

Definitions

  • My invention relates to hydraulic machines that can be used as pumps or motors in which means are provided to vary the delivery of fluids when the machine is used as a pump or vary the speed of the machine when it is usedas a motor. f
  • Another object is-to provide a pump or motor power transmission unit in which the friction between. working parts has been decreased to a minimum thereby insuring longer life "to the mechanism.
  • Figure 1 is a section on the line 1-1 of Figure 2 and shows the internal structure of my unit.
  • Figure 2 is a section taken on the line 2--2 of Figure 1 showing liquid passages and adjusting lever.
  • Figure 3 is a section taken on the line 3-3 of Figure 2 showing the distributor ring.
  • Figure 4 is a section on the line 4-4 of Figure 2 showing inlet and outlet channels.
  • Figure 5 is a section on the line 5-5 of Figure 9 showing radial channels to compression chambers.
  • Figure 6 is a section on the line 6-6 of Figure 7 showing an alternate distributor ring.
  • Figure 7 is a section on the line 7-7 of Figure 6.
  • Figure 8 is a diagrammatic view showing my hydraulic units arranged to form a transmission system.
  • Figure 9 is a side elevation of a modification of my unit when shaft is stationary and housing is rotated, with part in section. 1
  • Figure 10 is a front elevation of my shifting lever for varying the speed of transmission or volume of delivered fluid, as shown in Figure 2.
  • Figure 11 is a sectional view along the lines 11-11 of Fig. 9.
  • Blades or bafiies 5 are secured in the openings 50'. between the segments 4 by means of pins 5?).
  • the blades 5 extend from the segments 4 to other segments which are rotatably mounted in a" blade ring 7 and their ends 50 are slidably mounted in the spaces 6 between the segments 6a.
  • the blades extending between the segments control the movement of the blade ring and prevent the inner blade ring from rotating about its axis but permitting it to move bodily in a circular path. While the blades 5 and the segments 4 act as an integral unit, it is preferable to form them as separate parts which are thereafter secured together, since this facilitates accurate formationof the segments 4 to cylindrical contour so that they may accurately fit the pockets 41).
  • each of the sides 7a is concave. I do not, however, wish to limit myself to this particular number of sides. together with the inner circumference 1b of the main casing and the blades, form compression and expansion pockets 10 for the fluids passing through the pump or motor depending on the use to which the mechanism is put. In order to provide clearance for the reciprocating and oscillatory motion of the blades, I have provided pockets 7b in the blade ring. As has been mentioned, the blade ring does not rotate but only oscillates, moving bodily in a circular path. An outer race 8 of a roller bearing 8a is rigidly mounted in the blade ring and moves with it.
  • An inner race 8b is rigidly mounted on an adjustable eccentric bushing 9.
  • the amount of eccentricity of this bushing determines the diameter of the circular path through which the blade ring moves and the volume of fluid which passes through the unit on each revolution of the shaft, and in order to vary this eccentricity, I have provided a rectangular slot 10 in the eccentric bushing in which is mounted a rectangular block 11 fixed to the shaft 12.
  • the eccentric bushing is slidably mounted with relation to the rectangular block and shaft, having rollers 13 which are mounted between the Walls 10a of a rectangular opening in the bushing and the sides of the block
  • the position of the eccentric bushing is controlled by means of a pin 14 extending across the greatest length of the rectangular opening in the eccentric bushing.
  • This pin is slidably mounted in the rectangular block 11 and the shaft 12 and thus provides means for moving the eccentric bushing to vary the extent of motion of the blade ring.
  • This lever has a bifurcated end 15a for connecting it to a sliding rod 17 extending through opening 201) in the shaft and an opening in the rectangular block.
  • pins 151) which engage in a groove 170 on an enlarged end of the sliding rod for moving it to the right or left so that the rod is left free to rotate with the rectangular block and shaft.
  • the inner end 17a of the rod 1'7 a bell crank 18 is pivotally mounted by means of the pin 17b.
  • This bell crank 18 is fulcrumed on a pin 18a in a slot 18b in the rectangular block, and has a" rounded end 180 engaging in a slide 19 in thepin 14. "When the bell crank is rocked on its fulcrum the rounded end will move the pin and bushing to change the eccentricity of the bushing to a value corresponding to a desired speed or volume to be obtained. The movement of the bushing 9 results in a variation in the distance between the center of the shaft and the center of the bushing, and hence causes a variation of the amplitude of movementof the blade ring. By moving the bushing 9 across zero eccentricity the direction of rotation will be changed, if the unit is used as a motor. The same manipulation applied on the unit when used as a pump will reverse the direction of the flow of liquid.
  • the shaft 12 is rotatively mounted on ball bearings 21 fixed in the side plates at 21a. On its left end is shown fixedly mounted a coupling 22 for driving the shaft. I do not necessarily require a coupling, as a gear, pulley, or any other means for transmitting power to or from the shaft may be used.
  • a coupling as a gear, pulley, or any other means for transmitting power to or from the shaft may be used.
  • the shaft When the hydraulic mechanism is used as a motor the shaft may be used for driving a given machine. When the mechanism is used as a pump this shaft will be driven by a prime mover.
  • My unit is novel in the respect that it will function in two ways; that is. the shaft can be rotated or held stationary.
  • I provide driving means for rotating the housing when the unit is used as a pump, and means for utilizing the rotation of the housing for driving other mechanism when the unit is used as a motor and I obtain the reverse results of a condition in which the shaft is rotated.
  • FIGs 2, 3 and 4 I have illustrated a preferred valve system which controls the flow of fluids to and from the pump or motor.
  • fluids are drawn into the hole 23 and pass to an annular groove 24 within a hub 25 fixed to the main housing.
  • a distributor ring 26 is oscillated by an eccentric 2'! mounted on the shaft 12.
  • pins 28 Secured in the periphery of the distributor ring are pins 28 which are free to slide in pockets 29 in the hub 25. These pins prevent the distributor ring from rotating with the shaft and limit it in an eccentric bodily motion.
  • the fluid on leaving the annular groove passes through elongated curved slots or ports 30 in the distributor ring. These curved slots, as indicated in Figure 5, communicate with similarly arranged slots 31 in the side plates 3.
  • the slots 31 register memes with channels 32 which lead to the compression chambers 10.
  • the distributor ring and plate have the same 1 number of slots and their movement is timed to properly control the passage of fluid to and from the mechanism. While the distributor ring is oscillating its slots will periodically provide passages for the flow of liquid through the circular inlet groove in the hub 25 and through the curved slots in the plate 3. From these slots the fluid is drawn into the compression chamber through the channels 32 in the plate 3 by the suction caused by the motion of the blade ring enlarging the volume of these chambers.
  • the chambers 33a are in position to begin taking in fluid when the chambers 331) have reached the stage of complete expans'on and are ready to expel the fluid through the passages 32a in the compression chambers and back through the channels 32.
  • the channels 32 alterhate as intake and discharge passages. At any one time during the cycle of operation each of the chambers will be in part or complete expansion or compression position.
  • the distributor ring is timed with the movement of the blade ring so that its slots will periodically connect the channels 32 with the inlet and outlet grooves 24 and 34 respectively, in the hub 25 in the proper relation, and as shown is 90 ahead of the blade ring in its direction of rotation.
  • each chamber will alternately receive and discharge fluid and cause the blade ring to oscillate bodily thereby rotating the shaft 12 which can then drive a machine.
  • Figures 6 and '7 show an alternative valve system for controlling the flow of fluids.
  • I provide a disc 36 which is keyed to the shaft 12 and rotates with it.
  • this disc there are two semi-crcular slots 37 and 38.
  • the slots 37 and 38 will alternately align themselves with the inlet and outlet grooves 24 and 34 in the hub 25 and form open passages to the slots 31 and channels 32 in the plate 3 and permit the fluid to be directed properly during the cycle of operation.
  • Figure 6 I have indicated by arrows the direction of flow of the liquid for one partcular alignment of the valve. This same condition is repeated for each compression chamber while the shaft is rotating.
  • section 46 is a dividing wall between the pockets 45 and 48 and prevents the fluid from flowing directly from one to the other.
  • auxiliary storage tank 52 for retaining a certain amount of fluid.
  • This tank can be open or closed. depending upon the fluid used.
  • fluid from the storage tank is forced through the pipes 54 and 55 into the pipes49 and 51.
  • an adjustable back pressure valve 541 that operates automatically f to relieve the system of any excess pressure that may develop.
  • each unit I provides a ring and groove 56 to catch ailleaking fluid along the shaft and prevent its loss by pumping it back to the storage tank through the pipes 57 by another gear pump 58.
  • a machine of the class described comprising a cylindrical casing, a shaft iournaled axially in said casing, a rectangular block fixed centrally to said shaft within said casing, a disk having a diametrical transverse slot for receiving said block, means actuable while the machine is in operation for adjusting said disk along said slot to vary the eccentricity of said disk relative to said shaft, is member having an opening in which said disk is rotatably journaled, said member extending from end to end within said casing, and means connecting said member with the outer wall of said casing for preventing rotation of said member with said shaft and dividing the space between said member and outer casing walls into a plurality of expansible and contractible chambers.
  • a machine of theclass described comprising a casing, a shaft iournaled in said casing, a rectangular block fixed centrally to said shaft within said casing. a diskhaving a diametrical transverse slot for receiving said block, a bar extending through said block and hearing at opposite ends against the ends of said disk slot, a bell crank lever fulcrumed on said block and having one end engaging said bar, a member rotatable with said shaft and movable axially thereof engaging the other end of said lever for adjusting said bar lengthwise relative to said block and thereby the eccentricity of said disk relative to said shaft, a member within which said disk is journaled, and means including said member and easing defining variable capacity chambers alternately expanding and contracting by the rotation of said disk and to an extent determined by its eccentricity relative to said shaft.
  • a machine of the class described comprising a casing having an outer cylindrical wall and a pair of spaced parallel end walls, a shaft journaled centrally in said end walls and extending therefrom at one end, a ring slidable between said end walls, vanes connecting said ring with said cylindrical wall and defining with said casing walls and ring a plurality of expansible and contractible chambers, an eccentric journaled'in said ring, means connecting said eccentric to said shaft for adjustment of the eccentricity of said eccentric, means on the extended end of said shaft for transmitting torque through said shaft, movable means outside of said casing, and operative connections between said movable means and said eccentricity adjusting means extending into said casing and shaft from the end of said shaft opposite to said shaft extension.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • General Details Of Gearings (AREA)
US333452A 1929-01-18 1929-01-18 Variable capacity pump or motor Expired - Lifetime US1961592A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US333452A US1961592A (en) 1929-01-18 1929-01-18 Variable capacity pump or motor
DEM113336D DE547594C (de) 1929-01-18 1929-12-31 Fluessigkeitswechsel- und -wendegetriebe mit einem auf einer verstellbaren Exzenterscheibe angeordneten Ringkoerper zur Veraenderung des Rauminhaltes der Verdraengungszellen
GB335/30A GB334476A (en) 1929-01-18 1930-01-03 Improvements in hydraulic variable speed power transmitting mechanisms
FR687901D FR687901A (fr) 1929-01-18 1930-01-09 Perfectionnements aux mécanismes de transmission de force hydrauliques à vitesse variable

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US333452A US1961592A (en) 1929-01-18 1929-01-18 Variable capacity pump or motor

Publications (1)

Publication Number Publication Date
US1961592A true US1961592A (en) 1934-06-05

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US333452A Expired - Lifetime US1961592A (en) 1929-01-18 1929-01-18 Variable capacity pump or motor

Country Status (4)

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US (1) US1961592A (fr)
DE (1) DE547594C (fr)
FR (1) FR687901A (fr)
GB (1) GB334476A (fr)

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2418412A (en) * 1943-05-28 1947-04-01 Bendix Aviat Corp Pump and distributor mechanism
US2438245A (en) * 1944-03-21 1948-03-23 Bendix Aviat Corp System and means for returning leakage fluid to a main fluid supply
US2461116A (en) * 1944-07-07 1949-02-08 Jeffrey Mfg Co Hydraulic system for controlling the operation of rotary hydraulic motors
US2510609A (en) * 1946-12-23 1950-06-06 William W Tingle Variable capacity hydraulic rotary pump or motor
US2513447A (en) * 1946-05-17 1950-07-04 Brown And Brown Rotary pump or motor
US2513446A (en) * 1946-05-17 1950-07-04 Brown And Brown Pump or motor
US2525907A (en) * 1943-09-16 1950-10-17 Henry Packard White Rotary hydraulic pump
US2547645A (en) * 1945-11-15 1951-04-03 United Aircraft Corp Hydraulic pump
US2662375A (en) * 1947-10-14 1953-12-15 Vickers Inc Rotary pump and motor hydraulic transmission
US2755744A (en) * 1952-11-04 1956-07-24 Alvin G Halvorsen Rotary hydraulic ratio pump
US2933239A (en) * 1957-12-06 1960-04-19 Mcdonald L Stephens Gas compressor
US2992769A (en) * 1957-03-20 1961-07-18 Petty Lab Inc Rotary fluid compressors
US3299866A (en) * 1964-06-15 1967-01-24 Ted W Birk Rotary internal combustion engine
US3426693A (en) * 1966-05-02 1969-02-11 John W Palmer Pump
US3703344A (en) * 1970-01-30 1972-11-21 Teodoro Reitter Internal combustion rotary engine
US3779673A (en) * 1972-04-24 1973-12-18 Bendix Corp Fluid stepper motor
US3966365A (en) * 1972-11-10 1976-06-29 Tex Trans Inc. Hydraulic power transmission and braking system for vehicles
US4107992A (en) * 1977-02-04 1978-08-22 Veeder Industries, Inc. Fluid meter
US4239466A (en) * 1979-01-22 1980-12-16 Abbey Harold Rotary machine with adjustable means for its eccentric rotor
US4958992A (en) * 1986-10-27 1990-09-25 Notron Engineering Variable capacity swivelling vane pump
US5236318A (en) * 1991-10-18 1993-08-17 Tecumseh Products Company Orbiting rotary compressor with adjustable eccentric
WO2002044533A2 (fr) * 2000-11-17 2002-06-06 Honeywell International Inc. Turbine de récupération des pertes de gaz et compresseur
US6481988B2 (en) * 2000-03-31 2002-11-19 Otice Establishment Internal combustion engine
US20050178117A1 (en) * 2004-02-18 2005-08-18 Sauer-Danfoss Inc. Charge/auxiliary circuit for reducing power losses in hydrostatic systems
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine
US20110171051A1 (en) * 2005-03-09 2011-07-14 Fibonacci International, Inc. Rotary engine swing vane apparatus and method of operation therefor
WO2012052240A3 (fr) * 2010-09-28 2013-02-21 Mahle International Gmbh Pompe à ailettes à palettes à mouvement pendulaire
WO2021181324A1 (fr) * 2020-03-11 2021-09-16 L&T Technology Services Limited Système pour conférer un mouvement rotatif à une roue

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201102100D0 (en) * 2011-02-08 2011-03-23 Benest Roger S Small compressor
CN108087252B (zh) * 2017-12-28 2023-12-12 杭州顺阀阀门有限公司 泵阀一体机

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2418412A (en) * 1943-05-28 1947-04-01 Bendix Aviat Corp Pump and distributor mechanism
US2525907A (en) * 1943-09-16 1950-10-17 Henry Packard White Rotary hydraulic pump
US2438245A (en) * 1944-03-21 1948-03-23 Bendix Aviat Corp System and means for returning leakage fluid to a main fluid supply
US2461116A (en) * 1944-07-07 1949-02-08 Jeffrey Mfg Co Hydraulic system for controlling the operation of rotary hydraulic motors
US2547645A (en) * 1945-11-15 1951-04-03 United Aircraft Corp Hydraulic pump
US2513447A (en) * 1946-05-17 1950-07-04 Brown And Brown Rotary pump or motor
US2513446A (en) * 1946-05-17 1950-07-04 Brown And Brown Pump or motor
US2510609A (en) * 1946-12-23 1950-06-06 William W Tingle Variable capacity hydraulic rotary pump or motor
US2662375A (en) * 1947-10-14 1953-12-15 Vickers Inc Rotary pump and motor hydraulic transmission
US2755744A (en) * 1952-11-04 1956-07-24 Alvin G Halvorsen Rotary hydraulic ratio pump
US2992769A (en) * 1957-03-20 1961-07-18 Petty Lab Inc Rotary fluid compressors
US2933239A (en) * 1957-12-06 1960-04-19 Mcdonald L Stephens Gas compressor
US3299866A (en) * 1964-06-15 1967-01-24 Ted W Birk Rotary internal combustion engine
US3426693A (en) * 1966-05-02 1969-02-11 John W Palmer Pump
US3703344A (en) * 1970-01-30 1972-11-21 Teodoro Reitter Internal combustion rotary engine
US3779673A (en) * 1972-04-24 1973-12-18 Bendix Corp Fluid stepper motor
US3966365A (en) * 1972-11-10 1976-06-29 Tex Trans Inc. Hydraulic power transmission and braking system for vehicles
US4107992A (en) * 1977-02-04 1978-08-22 Veeder Industries, Inc. Fluid meter
US4239466A (en) * 1979-01-22 1980-12-16 Abbey Harold Rotary machine with adjustable means for its eccentric rotor
US4958992A (en) * 1986-10-27 1990-09-25 Notron Engineering Variable capacity swivelling vane pump
US5236318A (en) * 1991-10-18 1993-08-17 Tecumseh Products Company Orbiting rotary compressor with adjustable eccentric
US6481988B2 (en) * 2000-03-31 2002-11-19 Otice Establishment Internal combustion engine
WO2002044533A2 (fr) * 2000-11-17 2002-06-06 Honeywell International Inc. Turbine de récupération des pertes de gaz et compresseur
WO2002044533A3 (fr) * 2000-11-17 2003-01-30 Honeywell Int Inc Turbine de récupération des pertes de gaz et compresseur
US6584963B2 (en) 2000-11-17 2003-07-01 Honeywell International Inc. Throttle loss recovery turbine and supercharger
US7438543B2 (en) * 2003-11-08 2008-10-21 Beez Guenther Oscillating slide machine
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine
US20050178117A1 (en) * 2004-02-18 2005-08-18 Sauer-Danfoss Inc. Charge/auxiliary circuit for reducing power losses in hydrostatic systems
US7299629B2 (en) * 2004-02-18 2007-11-27 Sauer-Danfoss Inc. Charge/auxiliary circuit for reducing power losses in hydrostatic systems
US20110171051A1 (en) * 2005-03-09 2011-07-14 Fibonacci International, Inc. Rotary engine swing vane apparatus and method of operation therefor
US9057267B2 (en) * 2005-03-09 2015-06-16 Merton W. Pekrul Rotary engine swing vane apparatus and method of operation therefor
WO2012052240A3 (fr) * 2010-09-28 2013-02-21 Mahle International Gmbh Pompe à ailettes à palettes à mouvement pendulaire
WO2021181324A1 (fr) * 2020-03-11 2021-09-16 L&T Technology Services Limited Système pour conférer un mouvement rotatif à une roue

Also Published As

Publication number Publication date
DE547594C (de) 1932-03-24
GB334476A (en) 1930-09-04
FR687901A (fr) 1930-08-14

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