US3694114A - Fluid flow machine with axially biassed rotor assembly - Google Patents

Fluid flow machine with axially biassed rotor assembly Download PDF

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Publication number
US3694114A
US3694114A US102614A US3694114DA US3694114A US 3694114 A US3694114 A US 3694114A US 102614 A US102614 A US 102614A US 3694114D A US3694114D A US 3694114DA US 3694114 A US3694114 A US 3694114A
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chambers
rotor assembly
pressure
ports
rotor
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Karl Eickmann
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    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids

Definitions

  • the present invention is concerned with fluid flow machines of the type in which expanding and contracting working chambers are formed during rotation of the rotor in a stator housing.
  • Machines of this type include vane pumps, vane compressors, vane engines, vane transmissions, gear pumps, gear motors, trochoid pumps, trochoid motors, and like machines in which the rotor assembly, by which the expanding and contracting working chambers are formed, is pressed against the valve plate located at one end of the rotor assembly in order to reduce the leakage losses in the gap between the rotor assembly and the valve plate.
  • Machines of this type are disclosed in my US. Pat. Nos. 2,975,716 and 3,417,706.
  • the machines include rotor assemblies which can be operated at high pressure, and are comparatively tightly sealed.
  • comparatively high volumetric leakage losses occur in the gap between the rotor assembly and the valve plate.
  • Other leakage losses occur because vanes are not pressed outward with sufficient force against a surrounding cam ring by which they are moved into and out of corresponding slot chambers.
  • Another object of the invention is to reduce leakage losses by pressing vanes outward by fluid from high and low pressure ports in the valve plate.
  • valve plate Preferably additional control ports are provided in the valve plate for supplying high pressure fluid to the inner ends of the slot chambers during the reversal of the flow into and out of the same by the high pressure and low pressure ports of the valve plate.
  • One embodiment of the invention comprises a valve plate mounted in a housing and having a control face with high pressure and low pressure ports communicating with the inlet and outlet of the housing.
  • a rotor assembly is mounted in the housing and includes means for forming working chambers expanding and contracting during rotation, such as vanes in radial slot cham bers.
  • the rotor assembly has a first end portion, preferably a separate first end wall, sliding on the control face during rotation, and having passages therethrough cooperating with the high pressure and low pressure ports and communicating with the working chambers for connecting the same successively with the high pressure and low pressure ports.
  • the rotor assembly has a second end portion, preferably a second end wall, including cylinder chambers communicating with the working chambers, respectively, and pistons in the cylinder chambers so that the varying pressure in the working chambers urges the respective pistons out of the cylinder chambers.
  • a thrust bearing is mounted in the housing opposite the second end portion or end wall, and includes a rotary member against which the pistons are pressed so that the first end portion of the rotor assembly is pressed against the valve plate and leakage from the same is reduced.
  • the first end portion has other passages communicating with the inner ends of the slot chambers and connecting the same successively with the high pressure and low pressure ports so as to balance the pressure at the inner and outer ends of the vanes, the pressure at the outer ends of the same corresponding to the pressure of the adjacent working chamber.
  • the second end portion of the rotor assembly has other cylinder chambers communicating with the slot chambers, and pistons in the same are pressed against the rotary member of the thrust bearing so that the rotor assembly is pressed tightly against the control face of the valve plate.
  • FIG. 1 is an axial sectional view taken along the line 1-1 of FIG. 16 and illustrating a first embodiment of the invention
  • FIG. 2 is an axial sectional view illustrating a second embodiment of the invention
  • FIGS. 3 to 7 are axial sectional views illustrating the parts of the rotor assembly of the embodiment of FIG. 2 in separated positions;
  • FIG. 8 is a cross-sectional view taken on line VIII- VIII in FIG. 5;
  • FIG. 9 is a side elevation illustrating a detail of FIG. 2 on an enlarged scale
  • FIGS. and 11 are schematic cross-sectional views illustrating the action of forces acting onthe vanes of the machine
  • FIG. 12 is a cross-sectional view taken on line XII- XII in FIG. 1;
  • FIG. 13 is a cross-sectional view taken on line XII- XIII in FIG. 1;
  • FIGS. 14 and 15 are cross-sectional views taken on line XV in FIG. 1 and illustrating modifications of the embodiment of FIG. 1;
  • FIG. 16 is a cross-sectional view taken on line XVI- XVI in FIG. 1.
  • expanding and contracting working chambers are formed between the central rotor portion 20, and separate end walls 21 and 22, together with the inner surface of the eccentric cam ring 18.
  • Working chambers 23 to 28 are shown in FIG. 16, and while the illustrated embodiment includes vanes 19 mounted in slot chambers 78 in the central rotor portion 20, the working chambers could also be trochoid chambers, or gear chambers, or be formed by other means.
  • the working chambers 23 to 28 are separated from each other by the vanes 19.
  • the cam ring 18 is mounted on the housing 1 eccentric to the axis of the rotor shaft 12, so that during rotation of the rotor assembly 20, 21, 22 and 12, the working chambers 23 to 28 successively expand and contract during each revolution of the rotor assembly.
  • Shaft 12 is mounted in bearings 13 supported in end walls 11a and 11b of the housing 11.
  • Housing wall 110 is provided with inlet 128 and outlet 129 through which a working fluid is supplied and discharged.
  • a stationary valve plate 30 is mounted on housing wall 11a and has a control face confronting the rotor assembly, and cooperating with a first end wall 21 of the same,
  • the shape of the high pressure and low pressure ports 36 and 37 in valve plate 30 is best seen in FIG. 12, and it is apparent that these ports communicate with the inlet and outlet 128 and 129.
  • the second end wall 22 at the other end of the rotor assembly has cylinder chambers 31 and 32 in which pistons 39 are disposed.
  • the outer ends of pistons 39 abut a rotary circular ring 15 which is part of a ball bearing 14 having a stationary ring 16 mounted on housing wall 11b.
  • the rotor assembly 20, 21, 22 with vanes 19, is mounted between the thrust bearing 14, 15, 16 and valve plate 30, and it will be seen that pressure in the cylinder chambers 31, 32 will cause movement of the rotor assembly toward and against the control face of valve plate 30, while the parts 21, 20, 22 of the rotor assembly are pressed together.
  • cam ring 18 could be mounted for rotation in the housing, but in the illustrated embodiment, cam ring 11 is secured by a key 17 against turning movement, but is mounted in housing 11 for limited axial movement together with the rotor end walls 21 and 22 which abut against lateral annular faces of cam ring 18.
  • the vanes 19 move inward and outward in the slot chambers 78, and divide the space between the rotor assembly and'the cam ring 18 into working chambers 23 to 28.
  • the working chambers expand and contract cyclically, while fluid, partly under pressure flows through the working chambers.
  • cylinder chambers 31 are provided in the end wall 22, and passages 33 between each working chamber and a corresponding cylinder chamber 31, connect the working chamber with the cylinder chamber.
  • Pistons 39 preferably provided with sealing rings as best shown in FIG. 9 for the embodiment of FIG. 2, are axially slidable in the cylinder chambers 31, and abut the rotary ring 15 of the thrust bearing 14, 15, 16.
  • Passages 35 extend through the end wall 21, and have open ends cooperating with the valve plate 30, and with the ports 36 and 37, so that fluid enters the working chambers and is discharged from the same by means of ports 36 and 37 which communicate with the inlet and outlet 128, 129.
  • the fluid pressure acts in one axial direction against the pistons 39 in cylinder chambers 31 so that the respective pistons are pressed against the rotary ring 15 of the thrust bearing, and in the opposite axial direction toward the rotor end wall 22 so that the same is pressed against the central rotor end portion 20, which is pressed against the other rotor end wall 21 which is pressed against the control face of the valve plate 30.
  • the dimension of the cylinder chambers 31, and particularly the effective crosssection can be selected so that the axial pressure is sufficient for holding the parts i 21, 20, 22 of the rotor assembly together, so that no axially extending connecting bolts 77 are required.
  • the axial pressure also reduces the gap between the vanes 19 and the end walls 21, 22, and also the gaps between central rotor portion 20 and rotor end walls 21 and 22
  • a modification is illustrated in FIG. 14 in which the bolts 77 are omitted, which is possible by selecting the effective cross-sections of the cylinder chambers 31 and/or 32 accordingly rather large.
  • the effective crosssections of the cylinder chambers 31 and/or 32 must be sogreat that the total sum of the effective pressure area results in an axially acting pressure which is greater than the axial fluid pressure in the gap between valve plate 30 and rotor end wall 21.
  • the parts of the rotor assembly 20, 21, 22 are pressed together only by the fluid pressure in the cylinder chambers 31 and/or 32 and bolts 77 can be omitted.
  • the entire rotor assembly 20, 21, 22 is pressed as a whole against the control face of the valve plate, as in the embodiment of FIG. 15.
  • the cross-sections of the cylinder chambers 31 and 32 are shown to be comparatively small, since bolts 77 are provided through the rotor assembly.
  • the end wall 22' has much larger cylinder chambers 31', and also cylinder chambers 32' greater than the cylinder chambers 32 in the embodiment of FIG. 15.
  • the embodiment illustrated in the drawing employs slot chambers 78 in which vanes 19 controlled by cam ring 18 move in axial direction.
  • the rotor assembly can be constructed as a trochoid rotor, and the cam ring 18 can be replaced by a rotary ring having an inner trochoid surface so that between the rotating inner and outer trochoid rotors, trochoid working chambers are formed in a known way, whose volume is cyclically increased and decreased during rotation of the inner and outer rotors together.
  • the rotor end wall 21 may be omitted, since the trochoid working chambers directly communicate with the high pressure and low pressure ports 36 and 37 of the valve plate 30.
  • the trochoid rotor assembly is pressed against the valve plate 30 by the axial pressure exerted by pistons 39 due to the fluid pressure in cylinder chambers 31 in end wall 22.
  • the rotor assembly can also be constructed as a gear rotor in which event the cam ring 18 is replaced by a rotary inner gear ring.
  • a gear pump or motor is obtained, in which the inner and outer rotors are pressed in axial direction against the control face of the valve plate 30 due to the pressure in the cylinder chambers 31, and the resulting axial pressure of pistons 39 against the thrust bearing 14, 15, 16.
  • the gear rotor assembly need not have an end wall 21, since the working chambers of the gear rotor assembly cyclically communicate directly with the. ports 36 and 37 in valve plate 30.
  • a partition by which the high pressure working space and the low pressure working space of the gear rotor assembly are divided from each other, can be fitted between the inner and outer rotors, and secured to the valve plate 30.
  • each slot chamber 78 is in communication with a passage 38 passing through the rotor end wall 21, and having an open end cooperating with the ports 36 and 37 of the valve plate 30, so that during rotation of the rotor assembly, the passages 38 and their respective slot chambers 78 cyclically communicate with ports 36 and 37.
  • the ports of passages 38 which are best seen in FIG. 13, cooperate with additional ports provided in the valve plate 30.
  • a simple construction which is not illustrated in the drawing, is to provide an annular channel in valve plate 30 with which the passage 38 are connected during the entire revolution of the rotor assembly.
  • This annular channel not shown, must have such a radius as not to interfere with the passages 35, but is connected with the high pressure port 36 or 37.
  • the slot chambers 78 are at a all times filled with high pressure fluid, so that vanes 19 are continuously pressed outward against the inner surface of cam ring 19, so that the working chambers 23 to 28 between the vanes 19 are always separated from each other in the region of the outer ends of the vanes 19 so that leakage along the outer ends of the vanes 19 is eliminated. While this construction, not shown, is reliable and durable, the preferred construction of the invention shown in FIG.
  • FIG. 12 provides a connection of the slot chambers 78 with high pressure fluid only during a part of each rotor revolution.
  • the cross section of FIG. 13 shown that the passages 35 are located along a circle outward of the passages 38, which are staggered to the passages 35.
  • the passages 35 communicate with the working chambers 23 to 28, and the passages 38 communicate with the slot chambers 78, respectively, and more particularly with the inner ends of the same.
  • FIG. 13 shows the passages 38 radially inward of the passages 35, but it is also possible to place the ports of passages 38 radially outward of the ports of passages 35.
  • the passages 38, and thereby the respective slot chambers 78 are alternately provided with high pressure fluid and low pressure fluid since the ports 36, 37 are formed with radial bulges 51 and 52 which are swept by the ports of passages 38. Between the bulges 51 and 52 of ports 36 and 37, additional control ports 53 and 54 are provided so that not only bulges 51 and 52, but also control ports 53 and 54 are swept by the ports of passages 38.
  • the control ports 53 and 54 are provided which are located in the same circle as the bulges 51 and 52 and the ports of passages 38, and are consequently passed by the same.
  • the ports 36 and 37 are connected by ducts 55 and 58 with a double cylinder chamber 56 whose center portion is connected by a conduit 53 with control ports 54 and 53.
  • the piston 57 is operated by the pressures in ports 36 and 37, so that ports 53 and 54 are always connected with the port 36 or 37 which has the higher pressure since such higher pressure displaces the piston 57 in the double'piston chamber 56 to an outward position disconnecting the respective low pressure port from ports 53 and 54.
  • Each slot chamber 78 is connected with a cylinder chamber 32 by a conduit 34 in rotor end plate 22. As shown in FIGS. 14 and 15, the cylinder chambers 31 and 33 alternate in circumferential direction and are staggered in radial direction. While cylinder chambers 32 communicate with slot chambers 78, cylinder chambers 31 communicate through ducts 33 in the central rotor portion 20 and the end wall 22 with the respective working chamber of working chambers 23 to 28. A piston 39 is mounted in each cylinder chamber 32 and is pressed by the pressure in the.
  • the rotor assembly 481 includes a central rotor having a fixed side wall 483, a separate side wall 84, and two end walls 485 and 96.
  • the parts of the rotor assembly are best seen in FIGS. 3 to 7.
  • the slot chambers 93 for the vanes 79 extend into the side walls 84 and 483, and the ends of the vanes are located in these slot extensions.
  • Cylinder chambers 53 and cylinder chambers 99 are provided in end wall 96, together with portions of conduits 58 and 52.
  • Pistons 55 are mounted in cylinder chambers 53 and 99 for axial movement, and abut the rotary ring 9 of a thrust bearing 4 which has a stationary ring secured to the housing 1.
  • each slot chamber 94 communicates with a passage 42 in end wall 485, and with a conduit 52 in the other end wall 96 communicating with the cylinder chamber 99.
  • the rotor channel 42 connected with the slot chamber 93 is radially staggered to the passages 98 which communicate with the working chambers and rotor channels 97.
  • the high pressure and low pressure ports 482 and 583 of the valve plate 581 are correspondingly shaped and arranged, as explained with reference to the embodiment of FIG. 1.
  • FIGS. 2 to 9 is particularly suited for high pressure operations which is due to the fact that the vanes 79 have the axial ends thereof supported in the rotor side walls 483 and 84, as best seen in the lower portion of FIG. 2. Furthermore, the pressure in cylinder chambers 53 which corresponds to the pressure in the working chambers obtained under control of the valve plate 581, and the pressure in cylinder chambers 99, which corresponds to the pressure in the slot chambers 93, passages 42 and the corresponding port in valve plate 581, urge the rotor assembly toward and into abutment with the stationary valve plate 581.
  • a cam ring 7 cooperates with the outer ends of the vane 79 and is mounted by rollers 5 for rotations in the sleeve 6 in housing 1.
  • the slot chambers 79 or 93 may be used only for guiding the vanes, but it is also possible to use the same as hydraulic motors or pumps.
  • the construction shown in FIGS. 12 and 13 can also be used in the embodiment of FIG. 2.
  • the amount of fluid flowing through the slot chambers is added to the amount of fluid flowing through the working chambers and the output of the machine is correspondingly increased.
  • FIGS. 12 and 13 The amount of fluid flowing through the slot chambers is added to the amount of fluid flowing through the working chambers and the output of the machine is correspondingly increased.
  • FIGS. and 11 respectively correspond to FIGS. 30 and 31 of my US. Pat. No. 3,417,706.
  • FIG. 10 shows the rotor of a fluid handling device in accordance with my earlier US. Pat. No. 3,275,7I6. Vanes 409 are mounted in slots of the rotor side walls, and fluid under lower pressure acts from the left on the rotor and vanes, while fluid under high pressure, indicated by arrows 401 and 402 acts tangentially on the vanes on opposite sides of the rotor. The force of this pressure tends to brake the rotor segments toward the left. Rotor sectors between the slots are not held together on the outer periphery, and secured only by one bolt 405 or 406 and one integral portion 403 or 404.
  • Sectors 407, 408 are deflected toward the left in the direction of the arrows 414.
  • a small clearance opens a vent between the right face of vanes 409, 410 and the slot wall of the sector on the right thereof.
  • leakage fluid escapes out of the working chambers and slots, reducing the efflciency of the machine.
  • Fluid forces also act outwardly against the inner faces of the ring 412 in the direction of the arrows 413. Ring 412 radially surrounding the end walls of the rotor is deformed so that a small clearance appears so that leakage flow takes place.
  • an uninterrupted outer annular peripheral portion 91 of side wall 84 is provided which, together with the uninterrupted annular inner portion 404 keeps the whole rotor assembly together.
  • the uninterrupted portion 91 is short in tangential direction so that it cannot be deformed in radial outward or inward direction.
  • the bolts 89 fit into axial bores in the rotor assembly. Fluid forces 402 acting on the rotor assembly cannot tilt a sector of the same because there are no sectors.
  • the fitting bolts 89, and the uninterrupted inner and outer wall portions hold the rotor body and the end walls rigid in tangential direction, preventing clearances and leakages.
  • Fluid flow machine with axially biassed rotor assembly comprising a housing having an inlet and an outlet for a fluid; a valve plate mounted in said housing and having a control face with high pressure and low pressure ports communicating with said inlet and outlet; an actuating cam ring in said housing; a rotor assembly mounted in said housing for rotation about an axis, and being formed with angularly spaced substantially radial slot chambers, said rotor assembly including vanes mounted in said slot chambers for radial movement, respectively, and having outer ends sliding on said cam ring during rotation so that expanding and contracting working chambers are formed between said rotor assembly and said cam ring, said rotor as sembly having a first end portion formed with first passages for connecting during rotation said high pressure and low pressure ports successively with said working chambers, said first end portions being formed with second passages connecting during rotation said high pressure and low pressure ports successively with the inner ends of said slot chambers so as to balance the pressures at the inner and outer ends of said vanes, a
  • valve plate has in said control face additional control ports communicating with said high pressure port; and wherein said second passages cooperate with said additional control ports during rotation so that during reversal of the flow through said pressure ports, high pressure fluid flows through said control ports to said slot chambers.
  • Fluid flow machine with axially biassed rotor assembly comprising a housing having an inlet and an outlet for a fluid; a valve plate mounted in said housing and having a control face with high pressure and low pressure ports communicating with said inlet and outlet; a rotor assembly mounted in said housing for rotation about an axis, and including means for forming working chambers expanding and contracting during rotation, said rotor assembly having a first end portion sliding on said control face, and having passages therethrough cooperating with said high pressure and low pressure ports, and communicating with said working chambers, respectively, for connecting the same successively with said high pressure and low pressure ports, and a second end portion including cylinder chambers communicating with said working chambers, respectively, and pistons in said cylinder chambers so that the varying pressure in said working chambers urges the respective pistons out of said cylinder chambers; and a thrust bearing mounted on said housing opposite said second end portion and including a rotary member'against which said pistons are pressed whereby said first end portion of said rotor assembly is a
  • said rotor assembly includes a plurality of axially adjacent separate parts; and wherein the effective cross sections of said cylinder chambers have such a pressure area that the axial pressure acting on said rotor assembly in one direction to urge the same toward said control face of said valve plate is greater than the axial pressure exerted on said rotor assembly in the opposite axial direction by fluid in the gap between said control face and said first end portion of said rotor assembly whereby said parts are pressed together and against said control face.
  • said rotor assembly includes a rotor, and at least one end wall forming said first end portion; and wherein said passages penetrate said first end wall and open into said working chambers, respectively.
  • a machine as claimed in claim 5, comprising an eccentric cam ring mounted in said housing surrounding said rotor; wherein at least said rotor has angularly spaced substantially radial slot chambers; wherein said chamber forming means of said rotor assembly include vanes mounted in said slot chambers and having outer ends sliding on said cam ring during rotation; and wherein said one end wall has other passages therethrough communicating with the inner ends of said slot chambers, respectively, and connecting the same successively with said high pressure and low pressure ports so as to balance the pressure at the inner and outer ends of said vanes.
  • valve plate has in said control face additional control ports communicating with said high pressure port; and wherein said other passages cooperate with said additional ports during rotation so that during reverse of the flow through said pressure ports, high pressure fluid flows through said control ports to said slot chambers.
  • said second end portion includes other cylinder chambers communicating with said slot chambers, respectively, and wherein said rotor assembly includes other pistons in said other cylinder chambers pressed against said rotary member of said thrust hearing at a pressure depending on the pressure in the respective slot chambers.
  • said rotor assembly includes a central rotor, side walls at the ends of said central rotor having a greater diameter than the same, and first and second separate end walls forming said first and second end portions of said rotorassembly, said first end wall having said passages and said other passages, and said second end wall having said cylinder chambers and said other cylinder'chambers; wherein said slot chambers are formed in said central rotor and in said side walls; wherein said vanes have end portions located in said side walls; wherein said working chambers are formed by the central portions of said vanes around said central rotor between said side walls; and wherein said central rotor and said side walls have conduits connecting said working chambers with said passages in said first end wall and th 'd l d ch m ersin d d nd all.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US102614A 1970-01-15 1970-12-30 Fluid flow machine with axially biassed rotor assembly Expired - Lifetime US3694114A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844685A (en) * 1970-07-15 1974-10-29 K Eickmann Vane machine with pressure bias and balancing means for the rotary control port member
DE2514179A1 (de) * 1974-04-17 1975-11-06 Eaton Corp Druckmittelbetaetigte rotationskolbenmaschine
US4456430A (en) * 1978-10-25 1984-06-26 Karl Eickmann Vehicle employing a fluid motor with arrangements
US20070059195A1 (en) * 2005-09-15 2007-03-15 1564330 Ontario Inc. Rotary piston pump end pressure regulation system
WO2009010844A1 (en) * 2007-07-13 2009-01-22 Vanna Zaccarelli Machine for fluid pumping
US20090114046A1 (en) * 2005-11-16 2009-05-07 Jtekt Corporation Iron-base sintered part, manufacturing method of iron-base sintered part and actuator
US20110171054A1 (en) * 2009-06-25 2011-07-14 Patterson Albert W Rotary device
US20210108635A1 (en) * 2018-02-16 2021-04-15 Tcs Micropumps Limited Pump Apparatus

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2605360B1 (fr) * 1986-10-16 1991-04-12 Sulzer Ag Palette pour composant hydrostatique et composant hydrostatique le comportant
DE102011011384B4 (de) * 2011-02-17 2021-07-15 Festool Gmbh Hand-Werkzeugmaschine mit einem Lamellenmotor aus einem Nicht-Metall

Citations (6)

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Publication number Priority date Publication date Assignee Title
US858594A (en) * 1906-09-22 1907-07-02 Carl Gause Closing device.
US885783A (en) * 1906-12-15 1908-04-28 Cassius Clay Palmer Rotary compressor.
US2357334A (en) * 1941-03-29 1944-09-05 Manly Corp Fluid pressure device
US2641195A (en) * 1947-11-28 1953-06-09 Oilgear Co Sliding vave type hydrodynamic machine
US2787963A (en) * 1953-05-05 1957-04-09 Sundstrand Machine Tool Co Pump
US2927669A (en) * 1957-07-09 1960-03-08 Hans Putzer Compressed-air motor for a hoisting gear

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US858594A (en) * 1906-09-22 1907-07-02 Carl Gause Closing device.
US885783A (en) * 1906-12-15 1908-04-28 Cassius Clay Palmer Rotary compressor.
US2357334A (en) * 1941-03-29 1944-09-05 Manly Corp Fluid pressure device
US2641195A (en) * 1947-11-28 1953-06-09 Oilgear Co Sliding vave type hydrodynamic machine
US2787963A (en) * 1953-05-05 1957-04-09 Sundstrand Machine Tool Co Pump
US2927669A (en) * 1957-07-09 1960-03-08 Hans Putzer Compressed-air motor for a hoisting gear

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844685A (en) * 1970-07-15 1974-10-29 K Eickmann Vane machine with pressure bias and balancing means for the rotary control port member
DE2514179A1 (de) * 1974-04-17 1975-11-06 Eaton Corp Druckmittelbetaetigte rotationskolbenmaschine
US4456430A (en) * 1978-10-25 1984-06-26 Karl Eickmann Vehicle employing a fluid motor with arrangements
US20070059195A1 (en) * 2005-09-15 2007-03-15 1564330 Ontario Inc. Rotary piston pump end pressure regulation system
US7229262B2 (en) * 2005-09-15 2007-06-12 1564330 Ontario Inc. Rotary piston pump end pressure regulation system
US20090114046A1 (en) * 2005-11-16 2009-05-07 Jtekt Corporation Iron-base sintered part, manufacturing method of iron-base sintered part and actuator
US8491695B2 (en) * 2005-11-16 2013-07-23 Jtekt Corporation Iron-base sintered part, manufacturing method of iron-base sintered part and actuator
WO2009010844A1 (en) * 2007-07-13 2009-01-22 Vanna Zaccarelli Machine for fluid pumping
US20110171054A1 (en) * 2009-06-25 2011-07-14 Patterson Albert W Rotary device
US8602757B2 (en) 2009-06-25 2013-12-10 Albert W. Patterson Rotary device
US20210108635A1 (en) * 2018-02-16 2021-04-15 Tcs Micropumps Limited Pump Apparatus
US11542941B2 (en) * 2018-02-16 2023-01-03 Tcs Micropumps Limited Pump apparatus

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JPS5027881B1 (enrdf_load_stackoverflow) 1975-09-11

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