US3404634A - Pump - Google Patents

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Publication number
US3404634A
US3404634A US579976A US57997666A US3404634A US 3404634 A US3404634 A US 3404634A US 579976 A US579976 A US 579976A US 57997666 A US57997666 A US 57997666A US 3404634 A US3404634 A US 3404634A
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United States
Prior art keywords
fluid
pump
discharge
end plate
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
US579976A
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English (en)
Inventor
La Yern R Connelly
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.)
Eaton Corp
Original Assignee
Eaton Yale and Towne Inc
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 Eaton Yale and Towne Inc filed Critical Eaton Yale and Towne Inc
Priority to US579976A priority Critical patent/US3404634A/en
Priority to GB41239/67A priority patent/GB1182966A/en
Priority to DK459367AA priority patent/DK123371B/da
Priority to SE12688/67A priority patent/SE330834B/xx
Priority to NO169726A priority patent/NO120772B/no
Priority to CH1298267A priority patent/CH469196A/de
Priority to ES345455A priority patent/ES345455A1/es
Priority to DE19671653846 priority patent/DE1653846A1/de
Application granted granted Critical
Publication of US3404634A publication Critical patent/US3404634A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • 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
    • F04C2/34—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3445—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • 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
    • F04C2/34—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/91—O-ring seal

Definitions

  • An improved pump includes a resiliently deflectable sheet metal flange portion which is exposed to fluid at discharge pressure and cooperates with an end plate to provide a seal pressure therewith which increases with increases in pump discharge pressure to minimize leakage from the pump at high pressures.
  • a pressure chamber is provided opposite from a discharge chamber to minimize distortion or deflection of the parts of the pump.
  • a passage is formed in the pump to provide unimpeded fluid communication between a pumping chamber and a remote discharge chamber to minimize restrictions to the flow of fluid between a pumping means and a discharge chamber.
  • the present invention relates to a fluid pump, and more particularly relates to a fluid pump having improved means for communicating fluid to a discharge chamber thereof and for utilizing the discharge pressure of the pump to increase the volumetric efficiency thereof.
  • An object of the present invention is the provision of a new and improved pump which is constructed to provide for high discharge flows with a minimum of resistance and wherein fluid at discharge pressure is utilized to maintain parts of the pump in predetermined positions relative to each other at highdischarge pressures so that leakage of high pressure 'fluid between the parts is minimized and volumetric efiiciency of the pump is increased.
  • a further object of the present invention is the provision of a new and improved pump having a housing supporting a pumping means and wherein a flange portion of the housing and a part of the pump cooperate to form a chamber for fluid at substantially discharge pressure so that the pressure acting on the flange portion of the housing acts on the flange portion to increase the sealing pressure between the flange and the part of the pump as pressure in the chamber increases.
  • Yet another object of the present invention is the provision of a new and improved pump having rotary pumping means operable to pump fluid between inlet and discharge chambers of the pump and wherein a cover member is located on one axial side of the rotary pumping means and defines a discharge chamber of the pump and an end plate member is located on the other axial side of the pumping means and wherein the end plate member and housing define a chamber located so that fluid in the chamber acts on the end plate member urging the end plate member toward the rotary pumping means.
  • Still another object of the present invention is the provision of a new and improved pump, as noted in the next preceding paragraph, wherein the end plate member is provided with means for communicating fluid at substantially discharge pressure with the chamber.
  • Another object of the present invention is the provision of a new and improved pump having a rotor member which moves pumping elements along a cooperating cam surface of a cam member to effect pumping of a fluid and wherein conduit means for discharge fluid is provided in the cam member and includes a first passageway communicating fluid discharged at one axial side of the rotor to a discharge chamber at the other axial side of the rotor and a second passageway extending between the cam surface and the first passageway and wherein the passageways are effective to provide a high volumetricefficiency for the pump.
  • FIG. 1 is a sectional view, partially in elevation, of a pump embodying the present invention
  • FIG. 2 is a sectional view of the pump of FIG. 1, taken approximately along section line 2-2 thereof;
  • FIG. 3 is an enlarged fragmentary sectional view of a portion of the pump shown in FIG. 1;
  • FIG. 4 is a sectional view, taken approximately at line 4-4 of FIG. 1;
  • FIG. 5 is a sectional view, taken approximately at line 5--5 of FIG. 1;
  • FIG. 6 is an enlarged fragmentary sectional view of a portion of the pump of FIG. 2.
  • FIG. 1 A pump 10 embodying the present invention is shown in FIG. 1. While the pump 10 is preferably utilized in conjunction with a hydraulic power'steering system in an automotive vehicle and driven from an engine of the vehicle, it will become apparent from the following that the pump embodying the present invention may be utilized in many different applications.
  • the pump 10 includes a housing 11 supporting a pumping means 12 therein.
  • the pumping means 12 is a rotary pumping means secured to a driving shaft 13 for rotation therewith.
  • the pumpingmeans 12 includes a rotatable rotor member 14 secured to the shaft 13 and a stationary 'cam member 15 which is secured to the housing 11.
  • the rotor member 14 is an annular member having a plurality of radial slots therein which carry pumping elements 16.
  • the pumping elements 16 engage a surface 20 on the cam member 15 and define pumping pockets 21 therebetween.
  • the elements 16 are moved radially inwardly and outwardly of the rotor member 14 upon rotation thereof in pumping strokes.
  • the elements are moved radially by the cam surface and thereby effect pumping of fluid in a well-known manner.
  • the pumping means 12 is supported in the housing 11 closely adjacent a planar surface 24 of a cover member 25.
  • the cover member 25 includes inlet passageways 26, 26a therein which extend between the pumping means 12 and a fluid reservoir 30 of the pump.
  • the inlet passageways 26, 26a are spaced approximately 180 degrees apart in the cover member. Each passageway opens into the surface 24 at radially spaced locations to provide radially inner and outer inlet ports 28a, 2812, respectively, for the pumping means 12.
  • the cover member 25 also includes discharge passageways 27, 27a which communicate with the pumping pockets 21 and with an outlet fitting 31 which directs fluid discharged from the pump to the system.
  • the discharge passageways 27, 27a each open into the surface 24 at radially spaced locations to form pairs of radial inner and outer discharge ports 29a, 29b, respectively.
  • the radially inner ports 29a and the radially outer ports 29b are spaced approximately 180 degrees from each other in the cover member 25, and are spaced approximately degrees from the inlet ports 26, 26a.
  • Th cover member 25 additionally includes a central portion which provides a support for a bearing 32 which is operable to rotatably support an end 33 of the shaft 13 therein.
  • An end plate 35 is located on the axial side of the pumping means 12 opposite the axial side thereof at which thecover member is located.
  • the end plate 35 is fixed to the cover 25 by suitable screws 36 which extend through the cam member 15 and are threadedly engaged with the cover 25. The screws 36 maintain the end plate 35 in close proximity to the pumping means 12.
  • endplate 35, cam member and cover are additionally held in ra dially aligned elation by a locating pin 39 which extendst hrough the end plate 35, the cam member 15, and into the cover 25.
  • a locating pin 39 which extendst hrough the end plate 35, the cam member 15, and into the cover 25.
  • the subassembly formed by the end plate 35, cover 25 and cam member 15 is press fitted into the housing 11 and thereby held against movement relative to the housing.
  • the end plate includes an axially extending body portion 40 which rotatably supports the shaft 13 by means of a suitable bearing 44 and a radially extending web or flange portion 41 including an annular planar surface 42 located closely adjacent an axial side of the pumping means 12.
  • the body portion 40 of the end plate 35 is sealingly engaged with the housing 11 by means of. an O-ring seal 46 positioned between the body portion 40 and a flange portion 47 of the housing 11 which surrounds the outer peripheral surface of the body portion 40 and the seal 46.
  • An inner periphery of the body portion 40 of the end plate 35 is provided with a fluid seal means 50, shown schematically, located between the body portion and the shaft 13 to prevent leakage of fluid therebetween.
  • the flange or web portion 41 has a generally planar annular surface 42 which is positioned closely adjacent the pumping means 12, as previously noted.
  • the end plate 35 includes inlet passageways, generally indicated at 48, which are spaced 180 degrees apart therein and which communicate the pumping means 12 with the inlet passageways 26, 26a.
  • the inlet passageways 48 open into the surface 42 at radially spaced locations therein to provide radially outer and inner inlet ports 48a, 48b, respectively.
  • the inlet passageways 48 communicate with the inlet passageways 26, 26a in the cover member 25 by means of a flow passage 13a in the shaft 13 which opens into the inlet passageways 26, 26:: at the end 33 of the shaft 13.
  • the flow passage 13a in the shaft corn municates with the inlet passageways 48 through ports 13b, see FIG. 1, which extend radially through the shaft between the flow passage 13a and the inlet passageways 48.
  • the end plate 35 also includes groove portions or chambers 49a, 49b communicating with an axial side of the pumping pockets 21 of the pumping means 12. As shown in the drawings, the grooves or chambers 49a, 4% are spaced radially apart on the surface 42 and at 10- cations on the end plate corresponding to discharges of the pumping means.
  • the grooves 49a communicate with the discharge chambers 27, 27a in the cover member to provide a flow of discharge fluid from the pumping pockets to the discharge chambers by means which will be described in detail hereinafter.
  • the web or flange 41 also includes a port or channel 53 which extends therethrough from the chamber 49a at a discharge of the pumping means 12 and to a fluid chamber 54 defined by the end plate 35 and the housing 11, located to the left of the flange portion 41, as viewed in the drawings, and remote from the discharge chamber 27 and flow control valve means 28. It should be apparent from the above that the grooves 49a are in fluid communication with the discharge chambers 27, 27a as well as with the chamber 54.
  • Fluid from the reservoir 30 enters the inlet passages 26, 26a and is directed in part to the pumping means 12 through the inlet ports 28a, 28b in the cover member 25. Fluid in the passageways 26, 26a is also directed through the flow passage 13a in the shaft 13, the inlet passageways 48 in the end plate 35 and to the pumping means 12 through the ports 48a, 48b in the end plate.
  • Inlet fluid entering the pumping means 12 enters the pumping pockets 21 and is pumped through the discharge ports 29a, 29b and 49a, 49b in the cover member and end plate, respectively. The fluid flows from discharge ports 29a, 29b and 49a, 49b to the discharge passageways 27, 270i in'the cover member 25. Pumped fluid in the discharge passageways is directed therefrom to the system through the fitting 31.
  • the housing 11 is preferably composed of a resiliently deflectable metallic material. While, in the illustrated embodiment, the housing 11 is sheet metal, the housing may also be cast.
  • Fluid at discharge pressure in the chamber 54 additionally acts on a rear surface 60 of the web or flange 41 to urge the end plate 35 toward the pumping means 12. This pressure applies a force on the end plate acting toward the rotor and which opposes the pressure forces acting on the surface 42 of the end plate in a direction away from the rotor. It should be apparent from the foregoing description that the flange portion 41 of the end plate is exposed to axially acting pressure forces imposed thereon by fluid in the pumping pockets 21. Moreover, it should be apparent that the forces acting on the flange portion 41 vary from point to point thereon due to the changing pressure in the pockets 21 as the rotor member 14 rotates.
  • the high pressure in the chambers adjacent the discharge of the pumping means tends to produce localized distortions or deflections of the flange portion 41 which tend to move the surface 42 axially away from the pumping means. If distortion of the surface 42 occurs as described, leakage of fluid between the pumping pockets 21 along the interface between the surface 42 and the pumping means 12 will result to cause a decrease in volumetric efficiency of the pump.
  • the pressure in the chamber 54 balances the forces acting on the flange 41 and minimizes the localized deflections thereof to minimize the aforementioned leakage and maintain a high volumetric efliciency for the pump.
  • the pump 10 additionaly includes conduit means for freely communicating fluid discharged from the pumping pockets 21 of the pumping means 12 to the discharge chambers 27, 27a with a minimum of flow restriction to obtain a high volumetric efficiency of the pump.
  • the afore-mentioned conduit means includes an opening 57 extending through the cam member 15 between the radially outer chamber 49a in the end plate and the discharge chambers 27, 27a in the cover, as well as a port 58 extending radially between the cam surface 20 and the opening 57.
  • the opening 57 and port 58 provide an unimpeded flow path from the discharge of the pumping means adjacent the end plate 35 to the discharge chambers 27, 27a and with less resistance and less restriction of flow than if no such passages were provided.
  • the radially inner grooves or chambers 49b in the end plate 35 communicate with the discharge chambers 27, 27a through passageways formed by the portions of the pumping pockets 21 located radially inwardly of the pumping elements 16. It should be apparent from the above that a large flow area is provided for discharged fluid flowing from the grooves 49a, 49b to the discharge chamber to minimize restriction of the flow and, therefore, for a given amount of input power, the pump provides a higher output flow than if these passages were omitted.
  • the pump 10 additionally includes flow control means for metering the amount of fluid directed from the pump to the system through the fitting 31.
  • the flow control means 70 is operable to control the amount of fluid flowing to the system by by-passing fluid from the discharge passageways 27, 27a to the inlet passageways 26, 26a.
  • the flow control means includes a valve member 71 inovable between a first position wherein fluid in the discharge passageways 27, 27a is directed to the system and a second position wherein the valve member permits fluid communication between the inlet and discharge passageways to effect the abovementioned by-passing of discharged fluid.
  • the valve 71 is located so as to provide the fluid communication to effect by-passing of fluid to the pump inlet.
  • an improved pump which is constructed so that fluid at discharge or high pressure is utilized to provide a sealing pressure which increases with increases in pump discharge pressure to minimize leakage from the pump at high pressures.
  • the construction is further effective to minimize distortion or deflection of the parts of the pump which are remote from a discharge chamber thereof by providing a pressure balance to the parts, resulting in decreased internal leakage in the pump and maintenance of volumetric efficiency thereof at high pressures.
  • a pump constructed according to the invention is effective to provide unimpeded fluid communication between a pumping chamber and a remote discharge chamber thereof to minimize restrictions to the flow of discharged fluid flowing between the pumping means and the discharge chamber to further maintain volumetric efliciency of the pump at relatively high levels.
  • a fluid pump operable to pump fluid from an inlet to an outlet thereof and comprising a housing, rotary pumping means contained in said housing, shaft means extending into said housing and operable to drive said pumping means, means defining a fluid chamber including a resiliently deflectable flange portion of said housing, an end plate having a cooperating surface in engagement with said flange portion of said housing and providing a fluid seal therebetween, and means for communicating fluid at substantially discharge pressure to said chamber with said fluid pressure acting on said flange portion to deflect the same and to force said flange portion into tight sealing engagement with said surface and to increase said sealing pressure with increases in discharge pressure of said pumping means.
  • a fluid pump operable to pump fluid from an inlet to an outlet thereof and comprising a housing, rotary pumping means contained in said housing, shaft means extending into said housing and operable to drive said pumping means, means defining a fluid chamber including a resiliently deflectable flange portion of said housing, a cooperating surface in engagement with said flange portion and providing a fluid seal therebetween, means for communicating fluid at substantially discharge pressure to said chamber with said fluid pressure acting on said flange portion to force said flange portion into tight sealing engagement with said surface, and an end plate member surrounding said shaft and positioned adjacent said pumping means, said end plate member carrying a seal member which engages said flange portion, said flange portion defining one wall of said chamber and said chamber being additionally defined by a portion of said end plate member, said chamber being located so that fluid pressure in said chamber is effective to urge said end plate member toward said pumping means to minimize leakage between said end plate member and said pumping means.
  • a fluid pump operable to pump fluid from an inlet to an outlet thereof and comprising a housing, rotary pumping means contained in said housing, shaft means extending into said housing and operable to drive said pumping means, means defining a fluid chamber including a resiliently deflectable flange portion of said housing, a cooperating surface in engagement with said flange portion and providing a fluid seal therebetween, and means for communicating fluid at substantially discharge pressure to said chamber with said fluid pressure acting on said flange portion to force said flange portion into tight sealing engagement with said surface, said flange portion of said housing being constructed of sheet metal and said fluid pressure being effective to force said flange toward engagement with said surface and increase said sealing pressure with increases in discharge pressure of said pump.
  • a fluid pump for providing a supply of fluid to an external fluid system comprising a housing, rotary pumping means in said housing providing for pumping of said fluid between inlet and discharge passageways of said pump, said inlet and discharge passageways of said pump located adjacent each other at one axial side of said pumping means, an end plate member having a first surface adjacent said pumping means at an axial side thereof axially opposite from said one axial side of said pumping means and said inlet and discharge passageways, said first surface of said end plate member being exposed to fluid pressure in said pumping means, and conduit means for communicating fluid substantially at discharge pressure of said pumping means to a chamber formed within said housing at a second surface of said end plate member axially opposite from said first surface to urge said end plate member toward said one axial side of said pumping means and minimize deflection of said end plate member by said fluid pressure of said pumping means.
  • a pump as defined in claim 6 wherein said chamber is formed in part by a flange portion of said housing surrounding a peripheral surface on said. end plate mem her and in sealing engagement with said peripheral surface, said pressure in said chamber acting on said flange portion to produce a sealing pressure between said flange portion and said surface which increases in response to increased discharge pressure of said pumping means.
  • a fluid pump operable to direct fluid to a fluid system through a discharge passageway thereof and comprising a housing, rotary pumping means supported in said housing and including rotor means rotatable in said housing about an axis, a cam member surrounding said rotary pumping means, pumping rollers movable relative to a cam surface of said cam member and cooperating with said cam member and said rotor means to provide pumping pockets which vary in volume as said rotor means rotates, an end plate member forming a chamber at an axial side of said rotor means remote from said discharge passageway and operable to receive high pressure discharge fluid from said pockets, and conduit means operable to communicate fluid from said chamber to said discharge passageway in an unrestricted manner with said fluid flowing from said chamber to said discharge passageway with a minimum of flow resistance, said conduit means including a first fluid passageway extending between said chamber and said discharge passageway and a second fluid passageway in said cam member extending between said first passageway and said cam surface and communicating with said pockets.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US579976A 1966-09-16 1966-09-16 Pump Expired - Lifetime US3404634A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US579976A US3404634A (en) 1966-09-16 1966-09-16 Pump
GB41239/67A GB1182966A (en) 1966-09-16 1967-09-08 Improvements in or relating to Rotary Pumps.
DK459367AA DK123371B (da) 1966-09-16 1967-09-13 Pumpe.
NO169726A NO120772B (enrdf_load_html_response) 1966-09-16 1967-09-14
SE12688/67A SE330834B (enrdf_load_html_response) 1966-09-16 1967-09-14
CH1298267A CH469196A (de) 1966-09-16 1967-09-14 Rotations-Pumpe
ES345455A ES345455A1 (es) 1966-09-16 1967-09-15 Perfeccionamientos en las bombas de fluido.
DE19671653846 DE1653846A1 (de) 1966-09-16 1967-09-18 Pumpe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US579976A US3404634A (en) 1966-09-16 1966-09-16 Pump

Publications (1)

Publication Number Publication Date
US3404634A true US3404634A (en) 1968-10-08

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ID=24319130

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Application Number Title Priority Date Filing Date
US579976A Expired - Lifetime US3404634A (en) 1966-09-16 1966-09-16 Pump

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US (1) US3404634A (enrdf_load_html_response)
CH (1) CH469196A (enrdf_load_html_response)
DE (1) DE1653846A1 (enrdf_load_html_response)
DK (1) DK123371B (enrdf_load_html_response)
ES (1) ES345455A1 (enrdf_load_html_response)
GB (1) GB1182966A (enrdf_load_html_response)
NO (1) NO120772B (enrdf_load_html_response)
SE (1) SE330834B (enrdf_load_html_response)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479962A (en) * 1967-11-22 1969-11-25 Sperry Rand Corp Power transmission
US3491699A (en) * 1968-02-26 1970-01-27 Sperry Rand Corp Power transmission
US3711225A (en) * 1971-08-26 1973-01-16 Gen Motors Corp Epitrochoidal compressor
US3801239A (en) * 1972-04-03 1974-04-02 Eaton Corp Controller for fluid operated device
US4251190A (en) * 1979-02-08 1981-02-17 General Signal Corporation Water ring rotary air compressor
US4502854A (en) * 1982-03-23 1985-03-05 Diesel Kiki Co., Ltd. Vane compressor having rearwardly located suction connector and discharge connector
US4536133A (en) * 1984-03-22 1985-08-20 Zahnradfabrik Friedrichshafen, Ag. Regulatable vane pump
US4538976A (en) * 1983-04-25 1985-09-03 Diesel Kiki Co., Ltd. Vane compressor having suction port and discharge port located at the same axial side thereof
US20040037728A1 (en) * 2000-08-25 2004-02-26 Van Der Sluis Francis Maria Antonius Roller vane pump incorporating a bearing bush

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3170408A (en) * 1960-01-20 1965-02-23 Waterous Co Rotary pumps
US3204566A (en) * 1962-06-11 1965-09-07 Feroy Arne Vane type hydraulic mechanism with balanced stator walls
US3236566A (en) * 1963-03-20 1966-02-22 Chrysler Corp Hydraulic pump
US3253548A (en) * 1958-09-19 1966-05-31 Gen Motors Corp Pump
US3273503A (en) * 1963-12-26 1966-09-20 Trw Inc Stack up slipper pump and compact valve assembly
US3280754A (en) * 1964-02-12 1966-10-25 New York Air Brake Co Engine
US3311064A (en) * 1963-07-05 1967-03-28 Zahnradfabrik Friedrichshafen Vane-type rotary pumps
US3327636A (en) * 1965-04-30 1967-06-27 Ashtabula Bow Socket Company Fluid pump or motor structure

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3253548A (en) * 1958-09-19 1966-05-31 Gen Motors Corp Pump
US3170408A (en) * 1960-01-20 1965-02-23 Waterous Co Rotary pumps
US3204566A (en) * 1962-06-11 1965-09-07 Feroy Arne Vane type hydraulic mechanism with balanced stator walls
US3236566A (en) * 1963-03-20 1966-02-22 Chrysler Corp Hydraulic pump
US3311064A (en) * 1963-07-05 1967-03-28 Zahnradfabrik Friedrichshafen Vane-type rotary pumps
US3273503A (en) * 1963-12-26 1966-09-20 Trw Inc Stack up slipper pump and compact valve assembly
US3280754A (en) * 1964-02-12 1966-10-25 New York Air Brake Co Engine
US3327636A (en) * 1965-04-30 1967-06-27 Ashtabula Bow Socket Company Fluid pump or motor structure

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479962A (en) * 1967-11-22 1969-11-25 Sperry Rand Corp Power transmission
US3491699A (en) * 1968-02-26 1970-01-27 Sperry Rand Corp Power transmission
US3711225A (en) * 1971-08-26 1973-01-16 Gen Motors Corp Epitrochoidal compressor
US3801239A (en) * 1972-04-03 1974-04-02 Eaton Corp Controller for fluid operated device
US4251190A (en) * 1979-02-08 1981-02-17 General Signal Corporation Water ring rotary air compressor
US4502854A (en) * 1982-03-23 1985-03-05 Diesel Kiki Co., Ltd. Vane compressor having rearwardly located suction connector and discharge connector
US4538976A (en) * 1983-04-25 1985-09-03 Diesel Kiki Co., Ltd. Vane compressor having suction port and discharge port located at the same axial side thereof
US4536133A (en) * 1984-03-22 1985-08-20 Zahnradfabrik Friedrichshafen, Ag. Regulatable vane pump
US20040037728A1 (en) * 2000-08-25 2004-02-26 Van Der Sluis Francis Maria Antonius Roller vane pump incorporating a bearing bush
US6835056B2 (en) * 2000-08-25 2004-12-28 Van Doorne's Transmissie B.V. Roller vane pump incorporating a bearing bush

Also Published As

Publication number Publication date
CH469196A (de) 1969-02-28
NO120772B (enrdf_load_html_response) 1970-11-30
DE1653846A1 (de) 1971-06-09
SE330834B (enrdf_load_html_response) 1970-11-30
DK123371B (da) 1972-06-12
ES345455A1 (es) 1969-01-01
GB1182966A (en) 1970-03-04

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