US2832293A - Vane pump - Google Patents

Vane pump Download PDF

Info

Publication number
US2832293A
US2832293A US406127A US40612754A US2832293A US 2832293 A US2832293 A US 2832293A US 406127 A US406127 A US 406127A US 40612754 A US40612754 A US 40612754A US 2832293 A US2832293 A US 2832293A
Authority
US
United States
Prior art keywords
vanes
vane
rotor
fluid
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US406127A
Inventor
Cecil E Adams
Sun Yung Ho
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
American Brake Shoe Co
Original Assignee
American Brake Shoe Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by American Brake Shoe Co filed Critical American Brake Shoe Co
Priority to US406127A priority Critical patent/US2832293A/en
Application granted granted Critical
Publication of US2832293A publication Critical patent/US2832293A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08Rotary pistons
    • F01C21/0809Construction of vanes or vane holders
    • F01C21/0818Vane tracking; control therefor
    • F01C21/0854Vane tracking; control therefor by fluid means
    • F01C21/0863Vane tracking; control therefor by fluid means the fluid being the working fluid

Description

April 29, 1958 c. E. ADAMS ET AL 2,832,293

VANE PUMP Filed Jan. 26, 1954 s Sheets-Sheet 1 INVEN T 0R8 CECIL E. ADAMS BY YUNG H0 SUN April 1958 c. E. ADAMS ETAL 2,832,293

NE UMP iv v v INVENTORS 50 CECIL E. ADAMS BY YUNG HO SUN April 29, 1958 c. E. ADAMS ETAL 2,832,293

VANE PUMP Filed Jan. 26, 1954 3 Sheets-Sheet 3 INVENTO IS CECIL E. ADAM YUNG HO SUN BY nieni VANE PUlVlP Application January 26, 1954, Serial No. 406,127

'7 Claims. (Cl. 103-136) This invention relates generally to hydraulic apparatus and is more particularly directed to fluid pressure energy translating devices frequently designated as pumps and motors. Still more particularly, the invention is directed to fluid pressure energy translating devices of the vane type.

An object of this invention is to provide a vane type pump which will be particularly suited for operation at high pressures, the pump having means for urging the vanes into contact with parts of the pump casing under low forces so that the vanes will not engage the casing to such an extent as to mar the casing but will engage the same with suflicient force to prevent the flow of fluid under pressure from one side of the vanes to the other side. Another object of the invention is to provide a fluid pressure energy translating device having vanes of rela tively great thickness, the vanes having a pair of sealing edges for engaging the casing and the pump having means for substantially balancing the fluid pressure at the radially spaced ends of the vane, means also being provided for applying a low force to the vanes to urge them toward the casing wall to effect a double seal between the fluid transfer pockets formed by the vanes and the rotor and easing Walls.

A still further object of the invention is to provide a hydraulic pump having a plurality of circumferentiaily spaced radially extending vanes, the pump casing, the rotor and the vanes having means for conducting fluid under the same pressures to the inner and outer ends of the vanes, the rotor being provided with piston chambers under the vanes and piston pins in the piston chambers, the casing and rotor also being provided with passages for supplying fluid under pressure. to the inner ends of the piston pins to cause them to apply a low force to the vanes to urge them in an outward direction. A still further object of the invention is to provide a vane type fluid pressure energy translating device having a casing forming a rotor chamber, a rotor supported for rotation in the chamber by needle bearings carried by the casing, the casing also being provided with means for applying fluid under pressure to the needle bearings and with means for confining the fluid pressure to the regions containing the needle bearings, the casing being further provided with means for conducting fluid escaping past the confining means back to the inlet port to prevent excessive leakage from the pump.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a pre ferred form of embodiment of the invention is clearly shown.

In the drawings:

Fig. l is a vertical longitudinal sectional view taken through a fluid pump formed in accordance with the present invention.

Figs. 2 and 3 are vertical transverse sectional views recesses provide spaced sealing edges in engagementwithtaken on the planes indicated by the lines: II-II and III-III, respectively, of Fig. 1.

Fig. 4 is a detail sectional view taken through the pump and rotor to show the vane and piston pin construction employed in the pump.

Referring more particularly to the drawings, the numeral 20 designates the pump in its entirety. In the form of invention selected for illustration, a vane type pump of the unbalanced type has been employed. This pump includes a casing having end sections 21 and 22 and a spacer or cam section 23. The latter section has an opening 24 extending therethrough to form a rotor chamber when the sections 21, 22, and 23 are assembled. An unbalanced type of pump is employed in the present illustration and its opening 24 is substantially circular although the peripheral wall of the opening includes two parts 25 and 26 which are arcuate and have different radii struck from the axis of rotation of the pump shaft. These two parts 25 and 26 are interconnected by wall parts which are arcuate and have equal radii struck from center off-set from the axis of rotation of the shaft 27.

The casing sections 21 and 22 are provided with needle bearings 28 and 30 for rotatably supporting the shaft 27 in the casing. The section 21 has anopening for the shaft which extends completely through the section 21 so that the end of the shaft may project exteriorly of the casing to receive a pulley, a coupling or any other device for transmitting rotary motion from a prime mover to the pump. The section 21 has a sealing member 31 surrounding the shaft adjacent the outer end of the shaft opening. Between this sealing member and the needle bearing in the section 21, thecasing is provided with an annular r recess 32 for collecting fluid which may flow along the shaft or seep between a sealing member 33 and the shaft or casing. A passage 34 extends from the groove 32 to another recess 35 formed in the surface of the section 21 which engages the spacer 23.

A second sealing member 33 is provided in the section 22 to also confine fluid to the needle bearing 28 and the space around the shaft and center portion of the rotor. The section 22 has a recess 36 into which the inner end of the shaft 27 projects. This recess is connected also by a passage 37 with an inlet passage 38 formed in the section 22, the inlet passage 38 having a threaded port 40 to which fluid is supplied from a reservoir or any other suitable source in the operation of the pump. Section 22 has a second passage 41 which constitutes an outlet passage, this passage being threaded at its outer end, as at 42, for connection with a conduit leading to the point of use of the fluid delivered by the pump.

Section 21 has a recess 43 which registers with the passage 41, the recess and the passage being connected by holes 44 formed in the spacer 23. The recess 35 and passage 38 are also disposed in registration with one another and are connected by similar holes 44 formed in the spacer 23. The recesses 35 and 43 are provided so that, in the ope-ration of the pump, fluid will have unimpeded access to fluid transfer pockets 45 formed by the casing walls, the exterior Wall 46 of a rotor 47 and vanes 48 carried by the rotor and engaging the casing walls.

The rotor 47 is keyed to the shaft 27, as at 50, to rotate therewith, the rotor being disposed in the opening 24 formed in the spacer 23. The vanes 48 are of such width that they will have only a slight degree of clearance with the adjacent end faces of the sections: 21 and 22; the vanes must form a sliding seal with the faces of the sections. In the form of the invention shown, the vanes are relatively thick and have V-shaped recesses formed in the side edges and the outer end. These V-shaped assaeas the peripheral wall of the rotor chamber and with the side walls of such chamber, the spaced sealing edges providing a chamber at the outer end of each vane. This chamber is connected by the grooves in the side edges of the vanes with the inner ends of the slots formed in the rotor 47 to receive the vanes. These slots are precisely formed so that a close sliding fit is provided be tween the vanes and the rotor. By connecting the spaces at the inner and outer ends of the vanes, these members will be substantially pressure balanced, that is, the fluid pressures at the inner and outer ends will be equal and will be applied to end surfaces on the vanes which are also substantially equal; thus, when the fluid pump is exposed to fluid pressure in operation, these fluid pressures will not tend to urge the vanes in either direction.

As shown in Figs. 1 and 3, the end surfaces of the sections 21 and 22 have arcuate recesses disposed for registration with the inner ends of the vane slots in the rotor. These recesses, 51 and 52, are located adjacent and register with the inlet port 38 and outlet port 41, respectively, and extend throughout the same angle of rotation as such ports. Recess 51 is connected with the inlet port by slots 53 while recess 52 is connected with outlet port 41 by a slot 54. Recesses 51 and 52 will receive fluid at the pressures contained in the adjacent ports. The inner ends of the vane slots and the vanes will thus be exposed to the same pressures as the outer ends thereof when the vane slots register with the inlet and outlet ports. The sections 21 and 22 are further provided with grooves 55 for conducting fluid under outlet port pressure to the openings for the shaft and the needle bearings. This pressure is conducted through a groove 56 from one end to the other of the rotor, this groove 56 connecting with an annular groove 57 formed in the wall of the central opening in the rotor. The groove 57 is provided to conduct fluid under pressure to the inner ends of piston chambers formed in the rotor 47. These piston chambers extend radially from the groove 57 to the inner ends of the vane slots and slidably receive piston pins 60, these pins being employed to abut and urge the vanes, under a low force, toward the peripheral wall of the rotor chamber. In the form of the invention shown, one piston pin is provided for each vane. It is obvious that more piston pins could be employed if found desirable, also that the diameters of the piston pins could be varied from that shown when more or less force is required to urge the vanes in an outward direction. The pins selected for illustration are of a diameter less than the width of a vane and have been picked to exert a force which has been calculated to give the desired action; the size of the pins may be changed if more or less force is required to maintain the vanes in sealing engagement with the peripheral wall of the rotor chamber.

As previously pointed out, sections 25 and 26 of the peripheral wall are arcuate having their centers in the axis of rotation of the shaft 27. The sealing edges of the vanes will thus both engage the peripheral wall at these points and prevent or minimize the escape of fluid pressure from one side of the vane to the other. It is obvious that, when the vanes are adjacent the inlet and outlet ports, the pressures of these ports will exist on both sides of the vanes as well as within the recesses between the sealing edges of the vane. This pressure will also exist in the vane slots at the inner ends of the vanes since such slots register with the recesses connected with the inlet and outlet ports and the recesses at the outer ends of the vanes are also connected with the inner ends of the vane slots by the grooves in the ends of the vanes. As the vanes move across the sealing sections 25 and 26, the pressure in the space between the sealing edges of the vanes might vary due to some leakage of fluid across'the sealing edges. If this pressure varies, the pressures at the inner ends of the vanes will also vary due to the connection of the inner and outer ends of 4 the vanes through the slots formed in the side edges thereof.

The meeting faces of the sections 21 and 22 and the spacer 23 have annular grooves formed therein for the reception of sealing gaskets 62. These gaskets are compressed in these sealing grooves and serve to prevent the escape of fluid between the casing sections. The casing sections are clamped together by fastening devices 61 extending through aligned holes in the sections.

In the operation of the device as a unit, the rotor turns counter-clockwise as viewed in Fig. 2. The fluid transfer pockets increase in size during movement in the lower half of the rotor chamber, due to the eccentricity of the opening 24 relative to the rotor 46, and fluid is drawn through the inlet port 38 into the fluid transfer pockets. The continued rotation of the rotor carries the fluid in the transfer pockets across the sealing section 25 of the peripheral wall causing the transfer pockets to register with the outlet port and recess 41 and 43, respectively. As the transfer pockets continue to move, they decrease in size due to the eccentric relation of the rotor and chamber and fluid is expelled from the transfer pockets into the outlet port. Since this port is connected by groove 54, recess 52 and groove 55 with the space around the shaft, the outlet port pressure will exist in the space around the shaft and will be applied through grooves 56 and 57 to the inner ends of all of the piston pins 60.

When the apparatus is operating, pins 60 will be urged radially outwardly by fluid under pressure while the vanes 48 traverse the cam ring or opening 24 (counterclockwise as seen in Fig. 2) between the 10 and 2 oclock positions and when said vanes travel between the 2 and 10 oclock positions and across the outlet passage 41 they will be urged outwardly only by the centrifugal force of themselves and the pins 60. When the pins 60 are urged outwardly hydraulically they are transmitting the force of the fluid pressure to the vanes and causing the spaced sealing edges at the outer ends thereof to firmly engage the peripheral wall of the rotor chamber. Since the fluid pressures at the inner and outer ends of the vanes are substantially balanced at all times, the forces urged by the piston pins will be the only forces employed to urge the vanes in an outward direction in addition to the centrifugal force. By limiting the size of the piston pins, the force exerted thereby may also be limited. Since the force urging the vanes into engagement with the cam wall is thus restricted, the pressures developed by the pump may be increased to high valueswithout deleterious eflect.

While the form of embodiment of the present invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adapted, all coming within the scope of the claims which follow.

We claim:

1. In a fluid pressure energy translating device, a casing having side and peripheral walls forming a rotor chamber with circumferentially spaced inlet and outlet ports; a rotor supported for rotation in said chamber; vane elements projecting from said rotor and engaging said side and peripheral walls to form fluid transfer pockets; spaced sealing edges on the parts of the vane elements engaging said side and peripheral walls, the spaced edges providing each vane with a pressure chamber at its outer end connected with the space at the inner end of the vane; a piston pin disposed in said rotor in registration with each vane element; and means for applying fluid pressure from one of said ports to the inner ends of said piston pins to urge said vanes outwardly toward said peripheral wall.

2. In a fluid pressure energy translating device, a casing having side and peripheral walls forming a rotor chamber with circumferentially spaced inlet and outlet ports; a rotor supported for rotation in said chamber; spaced substantially radially extending vanes carried by said rotor and slidably engaging the peripheral wall of said chamber, said peripheral wall having sealing portions between said ports, said sealing portions being concentric with the axis of rotation of said rotor; spaced sealing edges on said vane elements for engaging said side and peripheral walls, the spaced sealing edges providing each vane with a pressure chamber at its outer end connected with the space at the inner end of the vane; a piston pin disposed in said rotor in registration with and at the inner end of each vane; and means for applying fluid pressure from one of said ports to the inner ends of said piston pins to urge said vanes toward said peripheral wall.

3. In a fluid pressure energy translating device, a casing having side and peripheral walls forming a rotor chamber with circumferentially spaced inlet and outlet ports; a rotor supported for rotation in said chamber; vane elements projecting from said rotor and engaging said side and peripheral walls to form iiuid transfer pockets; spaced sealing edges on the parts of the vane elements engaging said side and peripheral walls, the spaced edges providing each vane with a pressure chamher at its outer end connected With the space at the inner end of the vane; a piston pin disposed in said rotor in registration with each vane element, each of said piston pins having a cross-sectional area equal to a fractional part of the area of the inner end of the vane element registering therewith; and means for applying fluid pressure from one of said ports to the inner ends of said piston pins to urge said vanes outwardly toward said peripheral wall.

4. In a fluid pressure energy translating device of the vane type, structure for hydraulically urging the vanes of said device radially outwardly at least while said vanes traverse the low pressure port of said device, said fluid pressure energy translating device including a casing having a rotor chamber and low and high pressure ports; a rotor supported for rotation in said chamber, said rotor being disposed relative to the peripheral wall of the chamber to provide a fluid transfer section between said low and high pressure ports, said rotor having substantially radially extending vane slots; vanes disposed for reciprocatory movement in said slots independently of each other, each of said vanes having sealing means on its radially outer end engaging the peripheral wall of said chamber and surface means on the radially outer end of each vane presenting a first area to hydraulic pressure which urges said vane radially inwardly in its slot; means on each of said vanes presenting a second area to hydraulic pressure for urging said vane hydraulically outwardly radially in its slot; means for supplying pressure from said high pressure port to said second area while said vane traverses said high pressure port; means presenting a third area to hydraulic pressure for urging said vane hydraulically outwardly radially in its slot; means for conducting hydraulic fluid at equal pressures to said first and second areas, and means for conducting hydraulic fluid from said high pressure port to said third area, the hydraulic forces on said third area overbalancing the hydraulic forces on said first area and urging said vane radially outwardly in its slot and against the peripheral wall of said chamber at least While said vane traverses said low pressure port.

5. In a fluid pressure energy translating device of the vane type, structure for hydraulically urging the vanes of said device radially outwardly at least while said vanes traverse the low pressure port of said device, said fluid pressure energy translating device including a casing having a rotor chamber and low and high pressure ports; a rotor supported for rotation in said chamber, said rotor being disposed relative to the peripheral wall of the chamber to provide a fluid transfer section between said low and high pressure ports, said rotor having substantially radially extending vane slots; vanes disposed for reciprocatory movement in said slots independently of each other, each of said vanes having sealing means on its radially outermost end engaging the peripheral wall of said chamber and hydraulically operated means forurging each of said vanes radially outwardly in its slot, said hydraulically operated means including surface areas on opposite ends of the vane; means. for conducting pressures substantially equal to those at said low and high pressure ports to said opposite surface areas successively while said rotor and vane rotate in said chamber for at least partially balancing inward radial hydraulic thrusts on said vane; another hydraulically operated means for urging said vane radially outwardly against the peripheral wall of said chamber, and means for conducting fluid pressure from said outlet port to said other hydraulically operated means, said other hydraulically operated means urging said vane radially outwardly whenever the pressure on said opposite surface areas is less than the pressure in said outlet port.

6. In a fluid pressure energy translating device of the vane type, structure for hydraulically urging the vanes of said device radially outwardly at least while said vanes traverse the low pressure port of said device, said fluid pressure energy translating device including a casing having a rotor chamber and low and high pressure ports; a rotor supported for rotation in said chamber, said rotor being disposed relative to the peripheral wall of the chamber to provide a fluid transfer section be tween said low and high pressure ports, said rotor having substantially radially evtending vane slots; vanes disposed for reciprocatory movement in said slots independently of each other, each of said vanes having sealing means on its radially outermost end engaging the peripheral wall of said chamber and hydraulically operated means for urging each of said vanes radially outwardly in its slot, said hydraulically operated means presenting opposed surface areas to hydraulic fluid for causing opposite thrust forces to be applied radially to said vanes; means for conducting pressures substantially equal to those at said low and high pressure ports to said opposed surface areas successively while said rotor and vane rotate in said chamber for at least partially balancing inward radial hydraulic thrusts on said vane; another hydraulically operated means for urging said vane radially outwardly against the peripheral Wall of said chamber, and means for conducting fluid pressure from said outlet port to said other hydraulically operated means, said other hydraulically operated means urging said vane radially outwardly whenever the pressure on said opposite surface areas is less than the pressure in said outlet port.

7. In a fluid pressure energy translating device of the vane type including a rotor having radial slots and a rotor chamber having low and high pressure ports, that improvement comprising vanes mounted for reciprocation in said slots and mechanism for hydraulically urging each of said vanes outwardly in its radial slot at least while each vane traverses the low pressure port of said device, each of said vanes provided at its outer end with sealing means having sealing contact with the peripheral wall of said chamber and said outer end also having a first surface presenting a surface area to hydraulic pres sure for urging said vane radially inward in its slot, a second surface on each of said vanes presenting a surface area to hydraulic pressure urging said vane radially outward in its slot, means for supplying hydraulic pressure from said high pressure port to said second surface area while each of said vanes traverses said high pressure port, a third surface presenting a surface area to hydraulic pressure for urging said vane radially outward in its slot, means for conducting hydraulic fluid at equal pressures to said first and second surface areas, and means for conducting hydraulic fluid from said high pressure port to said third surface area, the hydraulic fluid supplied to said third surface area over-balancing the hydraulic pressure of said first surface area and urging said vane radially outward in its slot and against the peripheral wall of said amazes rotor chamber at least while said vane traverses said low pressure port.

References Cited in the file of this patent UNITED STATES PATENTS MacMillin et a1. Mar. 13, 1951 Hartmann Dec. 30, 1952 Rosaen Sept. 29, 1953 Kepka et a1. Aug. 9, 1955 Gassot Aug. 30, 1955 FOREIGN PATENTS Great Britain Aug. 15, 1935 Great Britain Apr. 5, 1938 Germany Apr. 4, 1938

US406127A 1954-01-26 1954-01-26 Vane pump Expired - Lifetime US2832293A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US406127A US2832293A (en) 1954-01-26 1954-01-26 Vane pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US406127A US2832293A (en) 1954-01-26 1954-01-26 Vane pump

Publications (1)

Publication Number Publication Date
US2832293A true US2832293A (en) 1958-04-29

Family

ID=23606645

Family Applications (1)

Application Number Title Priority Date Filing Date
US406127A Expired - Lifetime US2832293A (en) 1954-01-26 1954-01-26 Vane pump

Country Status (1)

Country Link
US (1) US2832293A (en)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2962973A (en) * 1958-07-23 1960-12-06 Vickers Inc Power transmission
US2962972A (en) * 1958-07-23 1960-12-06 Vickers Inc Power transmission
US2967489A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2967488A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3040974A (en) * 1956-12-11 1962-06-26 Basic Products Corp Rotary vacuum pumps
US3054357A (en) * 1958-08-07 1962-09-18 Daniel F Mcgill Dual pump power transmission
US3102494A (en) * 1961-02-23 1963-09-03 American Brake Shoe Co Rotary vane hydraulic power unit
US3214941A (en) * 1963-09-27 1965-11-02 Thor Power Tool Co Impulse tool
US3257958A (en) * 1965-03-29 1966-06-28 American Brake Shoe Co Rotary vane fluid power unit
US3279387A (en) * 1964-02-03 1966-10-18 Daniel F Mcgill Reversable pump and motor
US3312387A (en) * 1964-12-30 1967-04-04 Borg Warner Lubrication system for rotary compressor
US3362340A (en) * 1965-12-09 1968-01-09 Abex Corp Three-area vane type pressure energy translating device having shock absorbing valve means
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps
US3998001A (en) * 1976-02-05 1976-12-21 Marvin Glass & Associates Doll shower and bubble bath device
US4469474A (en) * 1980-04-04 1984-09-04 Compagnie De Construction Mecanique Sulzer Axially slidable vane motor with valves in fluid-based vanes
DE4109149A1 (en) * 1991-03-20 1992-09-24 Rexroth Mannesmann Gmbh Aluminium alloy control disc for vane cell pump
US5222886A (en) * 1991-03-20 1993-06-29 Mannesmann Rexroth Gmbh Cheek plate for a vane pump
US5449280A (en) * 1994-04-07 1995-09-12 Hypro Corporation Pump including integral reservoirs for permitting dry run of pump
US20110030822A1 (en) * 2009-08-07 2011-02-10 Bear Patrick A Dry Run Porting System
DE102010046591A1 (en) 2010-09-25 2012-03-29 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Vane pump

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB433488A (en) * 1934-04-26 1935-08-15 Frederick Llewellyn Smith Improvements in rotary pumps, engines, compressors or exhausters
DE658560C (en) * 1936-01-15 1938-04-04 Heinrich Aumann Device for canceling the effect of centrifugal force resulting from pressure of the separating slide on the inner Gehaeusewand in rotary engines
GB482750A (en) * 1936-10-05 1938-04-05 Stieger Helmut John Improvements relating to compressors, blowers and receivers for fluid pressure
US2251784A (en) * 1939-06-14 1941-08-05 Wagner Electric Corp Rotary compressor
US2335284A (en) * 1939-12-06 1943-11-30 Manly Corp Rotary fluid pressure device
US2423271A (en) * 1942-09-11 1947-07-01 Frank A Talbot Rotary motor, pump, and the like
US2499763A (en) * 1945-07-27 1950-03-07 William T Livermore Loose slipper rotary pump
US2545238A (en) * 1944-08-07 1951-03-13 Hpm Dev Corp Radial vane pump
US2623471A (en) * 1951-03-12 1952-12-30 Hartmann Mfg Company Vane type pump or motor
US2653551A (en) * 1947-12-22 1953-09-29 New York Air Brake Co Fluid pump
US2714858A (en) * 1950-11-03 1955-08-09 Kepka Frank Rotary compressors or pumps, in combination with hydraulic controls, and mechanical controls in co-ordination therewith
US2716469A (en) * 1947-10-23 1955-08-30 Gassot Rene Jean Louis Fluid brakes for rotary members

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB433488A (en) * 1934-04-26 1935-08-15 Frederick Llewellyn Smith Improvements in rotary pumps, engines, compressors or exhausters
DE658560C (en) * 1936-01-15 1938-04-04 Heinrich Aumann Device for canceling the effect of centrifugal force resulting from pressure of the separating slide on the inner Gehaeusewand in rotary engines
GB482750A (en) * 1936-10-05 1938-04-05 Stieger Helmut John Improvements relating to compressors, blowers and receivers for fluid pressure
US2251784A (en) * 1939-06-14 1941-08-05 Wagner Electric Corp Rotary compressor
US2335284A (en) * 1939-12-06 1943-11-30 Manly Corp Rotary fluid pressure device
US2423271A (en) * 1942-09-11 1947-07-01 Frank A Talbot Rotary motor, pump, and the like
US2545238A (en) * 1944-08-07 1951-03-13 Hpm Dev Corp Radial vane pump
US2499763A (en) * 1945-07-27 1950-03-07 William T Livermore Loose slipper rotary pump
US2716469A (en) * 1947-10-23 1955-08-30 Gassot Rene Jean Louis Fluid brakes for rotary members
US2653551A (en) * 1947-12-22 1953-09-29 New York Air Brake Co Fluid pump
US2714858A (en) * 1950-11-03 1955-08-09 Kepka Frank Rotary compressors or pumps, in combination with hydraulic controls, and mechanical controls in co-ordination therewith
US2623471A (en) * 1951-03-12 1952-12-30 Hartmann Mfg Company Vane type pump or motor

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3040974A (en) * 1956-12-11 1962-06-26 Basic Products Corp Rotary vacuum pumps
US2967489A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2967488A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2962972A (en) * 1958-07-23 1960-12-06 Vickers Inc Power transmission
US2962973A (en) * 1958-07-23 1960-12-06 Vickers Inc Power transmission
US3054357A (en) * 1958-08-07 1962-09-18 Daniel F Mcgill Dual pump power transmission
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3102494A (en) * 1961-02-23 1963-09-03 American Brake Shoe Co Rotary vane hydraulic power unit
US3214941A (en) * 1963-09-27 1965-11-02 Thor Power Tool Co Impulse tool
US3279387A (en) * 1964-02-03 1966-10-18 Daniel F Mcgill Reversable pump and motor
US3312387A (en) * 1964-12-30 1967-04-04 Borg Warner Lubrication system for rotary compressor
US3257958A (en) * 1965-03-29 1966-06-28 American Brake Shoe Co Rotary vane fluid power unit
US3362340A (en) * 1965-12-09 1968-01-09 Abex Corp Three-area vane type pressure energy translating device having shock absorbing valve means
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps
US3998001A (en) * 1976-02-05 1976-12-21 Marvin Glass & Associates Doll shower and bubble bath device
US4469474A (en) * 1980-04-04 1984-09-04 Compagnie De Construction Mecanique Sulzer Axially slidable vane motor with valves in fluid-based vanes
DE4109149A1 (en) * 1991-03-20 1992-09-24 Rexroth Mannesmann Gmbh Aluminium alloy control disc for vane cell pump
US5222886A (en) * 1991-03-20 1993-06-29 Mannesmann Rexroth Gmbh Cheek plate for a vane pump
DE4143466C2 (en) * 1991-03-20 1997-05-15 Rexroth Mannesmann Gmbh Control disc for vane pump
DE4109149C3 (en) * 1991-03-20 1999-01-14 Mannesmann Rexroth Ag Control disc for vane pump
US5449280A (en) * 1994-04-07 1995-09-12 Hypro Corporation Pump including integral reservoirs for permitting dry run of pump
US20110030822A1 (en) * 2009-08-07 2011-02-10 Bear Patrick A Dry Run Porting System
US9091261B2 (en) 2009-08-07 2015-07-28 Pentair Flow Technologies, Llc Dry run porting system
DE102010046591A1 (en) 2010-09-25 2012-03-29 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Vane pump
WO2012041283A2 (en) 2010-09-25 2012-04-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Vane cell pump
DE102010046591B4 (en) * 2010-09-25 2015-03-12 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Vane pump

Similar Documents

Publication Publication Date Title
US3924977A (en) Positive fluid displacement apparatus
US3223046A (en) Rotary radial piston machines
DE2661104C2 (en)
US2714856A (en) Rotary pump or motor
US3319575A (en) Piston
US2312891A (en) Hydrodynamic machine
US1961592A (en) Variable capacity pump or motor
US2612114A (en) Vane pump or motor
JP4597669B2 (en) Cam ring bearing for fluid delivery device
US2382042A (en) Positive displacement gear pump
US2255785A (en) Fluid pressure device
US2612110A (en) Pump and motor
US4411606A (en) Gerotor gear set device with integral rotor and commutator
US3311064A (en) Vane-type rotary pumps
US3752609A (en) Vane pump with fluid-biased end walls
US4087215A (en) Gerotor gearset device
US2098652A (en) Rotary pump
US2545238A (en) Radial vane pump
US2758548A (en) Rotary fluid displacement device and mechanism therefor
US6422845B1 (en) Rotary hydraulic vane pump with improved undervane porting
US6481992B2 (en) Vane pump
US2216053A (en) Rotary pump of the single rotor type
US2842064A (en) Hydraulic pressure unit
GB1273246A (en) Pressure loaded gear pump or motor
US2924182A (en) Fluid pressure energy translating device