EP0053868A2 - Pompe à piston à mouvement gyratoire - Google Patents

Pompe à piston à mouvement gyratoire Download PDF

Info

Publication number
EP0053868A2
EP0053868A2 EP81301961A EP81301961A EP0053868A2 EP 0053868 A2 EP0053868 A2 EP 0053868A2 EP 81301961 A EP81301961 A EP 81301961A EP 81301961 A EP81301961 A EP 81301961A EP 0053868 A2 EP0053868 A2 EP 0053868A2
Authority
EP
European Patent Office
Prior art keywords
pump
chamber
eccentric
exhaust
pump shaft
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.)
Withdrawn
Application number
EP81301961A
Other languages
German (de)
English (en)
Other versions
EP0053868A3 (fr
Inventor
Kazuichi Ito
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0053868A2 publication Critical patent/EP0053868A2/fr
Publication of EP0053868A3 publication Critical patent/EP0053868A3/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
    • 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
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/04—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type

Definitions

  • the present.invention relates to a rotary pump having an eccentric rotor adapted to make an eccentric movement relative to the axis of the pump shaft within a pump casing, so as to cause a pumping action in a pump chamber formed between a diaphragm mounted on the outer periphery of the eccentric rotor and an inner peripheral surface of the pump casing.
  • the pumping action is performed by an eccentric movement of the eccentric rotor so that the fluid discharged from the pump chamber is disadvantageously pulsated, and a diaphragm is deformed by the eccentric movement of the eccentric rotor to form the pump chamber, which causes an amount of deformation of the diaphragm to be varied whereby the volume of the pump chamber cannot be maintained constant to bring forth a change in quantity of discharge of the fluid.
  • a diaphragm is deformed by the eccentric movement of the eccentric rotor to form the pump chamber, which causes an amount of deformation of the diaphragm to be varied whereby the volume of the pump chamber cannot be maintained constant to bring forth a change in quantity of discharge of the fluid.
  • a pump casing 1 comprises a case body 3 composed of a pair of hollow cylindrical case halves 2, 2, and a pair of cover members 4, 5 adapted to close openings disposed at both ends of the case body 3, the case halves 2, 2 and the cover members 4, 5 being formed of synthetic resins such as polypropylene having chemical resisting properties and being integrally connected with each other by means of a plurality of connecting bolts 12.
  • a pump shaft 7 is inserted into a central portion of a cylindrical hollow chamber 6 defined within the pump casing 1, the pump shaft 7 being rotatably supported at its middle portion and inner end portion on the cover members 4, 5 through bearings 8, 9 and being connected to a prime mover (not shown) at its outer end extending ourward from one cover member 4 through a seal 10 so that the shaft 7 may be rotatably driven by the prime mover.
  • the pump shaft 7 is formed of with a pair/recessed grooves 11, 11 in axially spaced relation and circumferentially displaced in phase by 180 degrees, the recessed grooves 11, 11 having, as may be clearly shown in Fig. 2, driving planes 13, 13 disposed parallel to the central axis 0 of the pump shaft 7, and a pair of eccentric rotors /14, 14 internally peripherally provided with needle bearings 15, 15 are arranged to surround the pump shaft 7 at the position of the recessed grooves 11, 11.
  • Wedge members 16, 16 are interposed between the driving planes 13, 13 of the recessed grooves 11, 11 and inner peripheral surfaces 19, 19 of the needle bearings 15, 15, the wedge member 16 comprising a wedge roller 18 having a driven plane 17 bearing on the driving plane 13 of the recessed groove 11 and a clutch element 21 being fitted in the outer periphery of the wedge roller 18 and having a circular surface 20 having the same curvature as of the inner peripheral surface 19 of the needle bearing 15 and in intimate contact with the latter over its entire periphery.
  • the outer peripheral surface of the wedge member 16, that is, the circular surface 20 in the outer periphery of the clutch element 21 extends from the outer peripheral surface of the pump shaft 7 to cause the center A (Fig. 4) of the eccentric rotor 14 to be eccentric in a predetermined amount E relative to the central axis O of the pump shaft 7 through the needle bearing 15..
  • the pair of eccentric rotors 14, 14 effect their eccentric movement about the pump shaft 7 with a phase difference of 180 degrees through the wedge members 16, 16 and the needle bearings 15, 15 but the rotative force of the pump shaft 7 is not transmitted to the eccentric rotors 14, 14 by the action of the needle bearings 15, 15.
  • the clutch element 21 is subjected to a reaction from the inner peripheral surface 19 of the needle bearing 15 as the pump shaft 7 rotates and tends to pivot about the center O' of the wedge roller 18.
  • the center O' of the wedge roller 18 is deviated from the center A of the needle bearing 15 as described, the needle bearing 15 is subjected to a great radial pressing force from the clutch element 21 by said pivotal movement of the clutch element 21, thus decreasing a slip therebetween to minimize the wear.
  • the eccentric rotor 14 is wholly formed into a channel section from a pair of annular members 22, 22 having an L-shaped section, in outer peripheral portions of which are formed inwardly extending annular projections 23, 23.
  • An annular diaphragm 24 which is formed of a resilient material such as rubber and has an outer peripheral surface applied with teflon baking is radially slidably mounted on the outer periphery of the eccentric rotor 14, the disphragm 24 being slidably fitted in an annular hollow portion 25 of the eccentric rotor 14 of channel section and comprising a disc portion 27 provided with an annular engaging projection 26 engageable with an annular projection 23 formed in the outer periphery of the rotor 14 and an annular flange portion 28 integrally formed with the disc portion 27 at its external.
  • the annular flange portion 28 is at its end edge formed with radially outwardly extending annular engaging projecting elements 29, 29, which are brought into engagement with annular engaging grooves 30, 30 formed in both ends of each case half member 2 and are firmly fixedly held in position by means of annular stepped portions 31, 31 formed internally of the cover members 4, 5 and an annular stepped portion 33 in the outer periphery of a clamping ring 32 arranged between both the diaphragms24 and 24.
  • the engaging projecting elements 29, 29 formed on the outer periphral edge of the annular flange portion 28 of each diaphragm 24 are provided with engaging surfaces 29', 29' for prevention of disengagement.
  • Each engaging groove 30 of each case half member 2 and each annular stepped portion 33 in the outer periphery of the clamping ring 32 are also formed with an engaged surface 30' adapted to engage with said engaging surface 29' so that upon assembly of the pump casing 1, the engaging surface 29' is forced into engagement with the engaged surface 30' whereby the engaging projecting element 29 is immovably engaged by the engaging groove 30.
  • the outer peripheral surfaces of the annular flange portions 28, 28 of the diaphragms 24, 24 are urged against the inner peripheral surfaces of the cylindrical case halves 2, 2 by means of the wedge members 16, 16 through the eccentric rotors 14, 14.
  • the diaphragm 24 is pulled towards the center upon eccentric rotation of the eccentric rotor 14, but since the engaging projecting elements 29, 29 on the both end edges of the annular flange portion 28 are fixedly held by the annular engaging grooves 30, 30 of the case half 2, the annular stepped portion 31 of the cover body 4 or 5 and the annular stepped portion 33 of the clamping ring 32, no leakage of fluid within the pump chamber P occurs therefrom or no entry lubricating oil in the bearings8, 9 and needle bearings 15 into the pump chamber P occurs.
  • the case halves 2, 2 have partition grooves 35, 35 bored therein to open to the cylindrical hollow chamber 6, the partition grooves 35, 35 having partition members 36, 36 extended integrally with the annular flange portions 28, 28 of the diaphragms 24, 24,said partition members 36, 36 being radially slidably fitted in the partition grooves 35, 35 in fluid-tight manner.
  • the crescent-shaped pump /chambers P, P formed between the inner peripheral surafces of the case halves 2, 2 and the outer periperal surfaces of the diaphragms 24, 24 are divided by the partition members 36, 36 into an intake chamber Pi and an exhaust chamber Pe in fluid-tight manner, as shown by the two-dot contour lines in Fig.2.
  • Intake and exhaust passages39 and 40 axially spaced other from each/and extending in opposite directions are open to each of the partition grooves 35, the two exhaust passages 40, 40 being placed in communication with each other.
  • the partition member 36 is inclined relative to a plane 41 which passes through the central axis of the cylindrical member formed by the outer peripheral surface of the diaphragm 24, that is, the central axis A of the eccentric rotor 14.
  • the partition member 36 is formed at both sides thereof with intake and exhaust ports 42, 43 which are respectively open to the intake and exhaust chambers Pi, Pe and in communication with theintake and exhaust passages 39, 40, respectively.
  • the intake and exhaust ports 42, 43 are arranged so that the intake port 42 is on the side of the exhaust chamber Pe and the exhaust port 43 is on the side of the intake chamber Pi with respect to the plane which passes through the central point between the portsand the central axis O of the cylindrical hollow chamber 6, that is, the plane 41 which passes through a tangent between the outer peripheral surface of the diaphragm 24 and the inner peripheral surface of the case half member 2 to define the pump chamber P within the cylindrical hollow chamber 6 when the diaphragm 24 is positioned shown by the solid line in Fig. 2.
  • the communication between the intake and exhaust ports 42, 43 may be cut off at all times during rotation of the pump shaft 7 to reduce the pulsation of fluids supplied under pressure from the pump as small as possible, as will be described hereinafter.
  • reference numeral 44 designates a spacer interposed between the pair of needle bearings 15 and 15 and between the pair of eccentric rotors 14 and 14.
  • the eccentric rotors 14, 14 revolve with the phase difference of 180 degrees from each other within the cylindrical hollow chamber 6 eccentrically with respect to the pump shaft 7 whereby one part of the central portion of the annular flange portions 28, 28 in the outer periphery of the pair of diaphragms 24, 24 mounted on the outer periphery of the eccentric rotors 14, 14 is pressed against the inner peripheral surface of the case halves 2, 2 by the wedge members 16, 16 while the other part of the central portion of the annular flange portions 28, 28 the crescent-shaped gaps, that is, the pump is pulled toward the center to form/chambers P, P between the outer peripheral surface of the annular flange portions 28, 28 and the inner peripheral surface of the case halves 2, 2.
  • each pump chamber P is formed integral with the outer periphery. of the diaphragm 24 and divided into the intake chamber Pi and the exhaust chambers Pe in fluid-tight manner by the partition member 36 fitted in the partition groove 35 of each case half member 2. The volumes of these intake and exhaust chambers are changed by the eccentric rotational motion of the eccentric rotors 14,14 to cause a pumping action.
  • each eccentric rotor 14 In the state in which each eccentric rotor 14 is positioned at the top dead center of its stroke which is closest of the intake port 42 and exhaust port 43, i.e., the intermediate position between the intake and exhaust ports 42, 43, the intake chamber Pi leading to the intake port 42 is minimized in volume and is just to commence its stroke, whereas the exhaust chamber Pe leading to the exhaust port 43 is expanded in volume to the maximum and is just to commence its delivery.
  • the eccentric rotor 14 is rotated from this state in the manner described before, the volumes of the intake chamber Pi is gradually increased so as to suck the fluid thereinto whereas the exhaust chamber Pe is gradually decreasedin its volume to come into communication with the exhaust port 43, so that the fluid in the chamber Pe is compressed and delivered under pressure through the exhaust port 43.
  • the intake chamber Pi and the exhaust chamber Pe are just on the median position of the intake and exhaust strokes, respectively, where the volumes thereof come substatially equal to each other.
  • the intake chamber Pi further increases its volume
  • the exhaust chamber Pe decreases its volume, so that these chambers come to resume the state as shown by the solid line in Fig. 2, thus completing the suction and delivery strokes.
  • One cycle of suction and delivery strokes may be achieved by one rotation of the eccentric rotor 14, and a fluid of a volume equal to the volume of the pump chamber P is exhausted in one cycle.
  • the discharges flow rate ⁇ 1 representative of the quantity of discharge per unit time of one pump chamber P is obtained relative to the rotational angle e of the pump shaft 7.
  • the center of the eccentric rotor 14, i.e. the center A of the outer peripheral circle C in the central portion of the annular flange portion 28 of the diaphragm 24 rotates at a uniform speed relative to the axis O of the pump shaft 7 and therefore, the discharge flow rate ⁇ 1 is proportional to the distance y from the intersection D between the outer peripheral circle C and the line 00" (Y axis) connecting the center O" of the exhaust port 43 to the axis O of the pump shaft 7, to the exhaust port 43.
  • ⁇ 1 k y (k is the proportional constant)
  • the discharge flow eate ⁇ 2 of the pump chamber P different in phase by 180 degrees from the rate ⁇ 1 is given by Accordingly, the discharge flow rate ⁇ 1 of one pump chamber P is shown by the curve I of Fig. 5, whereas the discharge flow rate ⁇ 2 of the other pump chamber P different in phase by 180 degrees from the former is shown by the curve II of Fig. 5.
  • the fluid fed under pressure from the pump chamber P involves no pulsation to provide a constant flow rate.
  • a pump shaft rotatably journalled on a pump casing has a pair of eccentric rotors fitted thereon through bearings in an axially spaced relation and with a phase difference of 180 degrees in a peripheral direction, diaphragms are mounted on the outer periphery of the eccentric rotors to define a pair of pump chambers between the inner peripheral surface of the pump casing and the outer periphery of the diaphragm, the pump chamber being divided by a partition member into an intake chamber and an exhaust chamber in fluid-tight manner, and a communication between an intake port and an exhaust port which are respectively in communication with the intake chamber and the exhaust chamber is cut off by the partition member during the rotation of the pump shaft.
  • the communication between the intake port and exhaust port may be cut off at all times during the suction and delivery strokes of the pump chamber to avoid interruption of the suction and delivery strokes caused by the communication therebetween thus providing the continuous suction and delivery strokes
  • the rotational phase of the pair of the eccentric rotors may be diviated by 180 degrees to thereby differentiate the phase between both the intake and exhaust chambers through 180 degrees and the fluids fed under pressure from the exhaust chambers may be merged together to eliminate the pulsation of individual fluids diviatedin phase by'180 degrees and to provide a substantially constant overall discharge quantity from the exhaust port.
  • the pump chamber formed between the inner peripheral surface of the pump casing and the outer peripheral surface of the diaphragm is closed by the diaphragm, fluid within the pump chamber may not be leaked into and out of the pump casing and lubricating oil for the bearings or the like within the pump casing may not be entered into the pump chamber, as a consequence of which components disposed within the pump casing are not subjected to the action of corrosion and the like thus increasing the durability, and the fluids within the pump chamber are neither affected nor contaminated by being mixed with lubricating oil for the bearingsor the like and may be maintained clean.
  • the aforementioned diaphragm is formed at its outer peripheral edge with annular engaging projecting elements having an engaging surface for prevention of disengagement
  • the pump casing is provided with annular engaging grooves having an engaged surface for engagement with the engaging surface
  • the engaging projecting elements are, upon assembly of the pump casing, pressed against and engaged with the annular engaging grooves so that the outer peripheral edge of the diaphragm is fixedly held by the pump casing.
  • the outer peripheral edge of the diaphragm may be evenly secured to the pump casing over the entire periphery thereof without using specific fastening means such as bolts, a heavy load is imposed on the diaphragm by the eccentric motion of the eccentric rotors but an excessive load is not imposed locally on the outer periphery thereof or a stress is not concentrated thereon, thus increasing the durability.
  • the rotary pump comprises a pump shaft, a wedge member interposed between the pump shaft and a bearing fitted on the outer periphery thereof, a wedge roller having a driven plane bearing on a driving plane of a recessed groove formed in the pump shaft and being arranged eccentrically with respect to the center of an eccentric rotor, and a clutch element having a circular surface rotatably fitted in the outer periphery of the wedge roller and in surface contact with the inner peripheral surafce of the bearing.
  • the circular surface in the outer periphery of the clutch element and the inner peripheral surface of the bearing are in surface contact with each other and the contact area is large so that wearing therebetween may be considerably reduced, and as a result, the durability of the wedge member may be improved to effectively prevent the lowering of the pumping efficiency resulting from decrease in eccentricity of the eccentric rotors.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
EP81301961A 1980-12-06 1981-05-05 Pompe à piston à mouvement gyratoire Withdrawn EP0053868A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP172478/80 1980-12-06
JP17247880A JPS5797090A (en) 1980-12-06 1980-12-06 Rotary pump

Publications (2)

Publication Number Publication Date
EP0053868A2 true EP0053868A2 (fr) 1982-06-16
EP0053868A3 EP0053868A3 (fr) 1983-08-03

Family

ID=15942724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81301961A Withdrawn EP0053868A3 (fr) 1980-12-06 1981-05-05 Pompe à piston à mouvement gyratoire

Country Status (2)

Country Link
EP (1) EP0053868A3 (fr)
JP (1) JPS5797090A (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986005241A1 (fr) * 1985-02-27 1986-09-12 Gutag Innovations Ag Machine a deplacement positif, notamment pompe, et procede pour sa fabrication
FR2631081A1 (fr) * 1988-05-05 1989-11-10 Knf Neuberger Gmbh Pompe a membrane annulaire
EP0819853A3 (fr) * 1996-07-15 1998-09-02 Charles Austen Pumps Ltd Pompe rotative
US7198883B2 (en) 2004-09-24 2007-04-03 Agfa-Gevaert Processless lithographic printing plate
WO2019016522A1 (fr) * 2017-07-19 2019-01-24 Charles Austen Pumps Ltd. Pompe à déplacement positif à membrane rotative
WO2019016518A1 (fr) * 2017-07-19 2019-01-24 Charles Austen Pumps Ltd. Pompe volumétrique à membrane rotative
DE102019213611A1 (de) * 2019-09-06 2021-03-11 Ebm-Papst St. Georgen Gmbh & Co. Kg Orbitalpumpenvorrichtung mit Bombierung zum Fördern von flüssigem Medium sowie Verfahren und Verwendung

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009243349A (ja) * 2008-03-31 2009-10-22 Nidec Sankyo Corp ロータリーダイヤフラムポンプ

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE571668C (de) * 1929-05-23 1933-03-03 Edouard Godillot Drehkolbenverdichter, Pumpe usw. mit umlaufendem Gehaeuse
GB671094A (en) * 1949-08-17 1952-04-30 Vanton Pump Corp Rotary pumps
FR1095539A (fr) * 1953-12-10 1955-06-03 Pompe rotative
US2946291A (en) * 1957-01-14 1960-07-26 Roebig Christ & Co Inc Suction and pressure pump
LU39826A1 (fr) * 1961-02-24 1961-04-24
GB2018900A (en) * 1978-04-11 1979-10-24 Ito Kazuichi Rotary positive displacement fluid-machines
US4219314A (en) * 1979-01-22 1980-08-26 Thermo King Corporation Rolling piston rotary compressor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE571668C (de) * 1929-05-23 1933-03-03 Edouard Godillot Drehkolbenverdichter, Pumpe usw. mit umlaufendem Gehaeuse
GB671094A (en) * 1949-08-17 1952-04-30 Vanton Pump Corp Rotary pumps
FR1095539A (fr) * 1953-12-10 1955-06-03 Pompe rotative
US2946291A (en) * 1957-01-14 1960-07-26 Roebig Christ & Co Inc Suction and pressure pump
LU39826A1 (fr) * 1961-02-24 1961-04-24
GB2018900A (en) * 1978-04-11 1979-10-24 Ito Kazuichi Rotary positive displacement fluid-machines
US4219314A (en) * 1979-01-22 1980-08-26 Thermo King Corporation Rolling piston rotary compressor

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986005241A1 (fr) * 1985-02-27 1986-09-12 Gutag Innovations Ag Machine a deplacement positif, notamment pompe, et procede pour sa fabrication
US4789315A (en) * 1985-02-27 1988-12-06 Gutag Innovations Ag Positive displacement machine, more particularly pump, and method for fabricating such pump
FR2631081A1 (fr) * 1988-05-05 1989-11-10 Knf Neuberger Gmbh Pompe a membrane annulaire
EP0819853A3 (fr) * 1996-07-15 1998-09-02 Charles Austen Pumps Ltd Pompe rotative
US7198883B2 (en) 2004-09-24 2007-04-03 Agfa-Gevaert Processless lithographic printing plate
WO2019016522A1 (fr) * 2017-07-19 2019-01-24 Charles Austen Pumps Ltd. Pompe à déplacement positif à membrane rotative
WO2019016518A1 (fr) * 2017-07-19 2019-01-24 Charles Austen Pumps Ltd. Pompe volumétrique à membrane rotative
CN111183286A (zh) * 2017-07-19 2020-05-19 查莱斯奥斯藤泵有限公司 旋转隔膜正排量泵
CN111183286B (zh) * 2017-07-19 2022-05-27 查莱斯奥斯藤泵有限公司 旋转隔膜正排量泵
US11499551B2 (en) 2017-07-19 2022-11-15 Charles Austen Pumps Ltd. Rotary diaphragm positive displacement pump
DE102019213611A1 (de) * 2019-09-06 2021-03-11 Ebm-Papst St. Georgen Gmbh & Co. Kg Orbitalpumpenvorrichtung mit Bombierung zum Fördern von flüssigem Medium sowie Verfahren und Verwendung

Also Published As

Publication number Publication date
JPS5797090A (en) 1982-06-16
EP0053868A3 (fr) 1983-08-03

Similar Documents

Publication Publication Date Title
US11506056B2 (en) Rotary machine
US3431863A (en) Guide means
US2832293A (en) Vane pump
US3125032A (en) Rotary pump
US4836759A (en) Rotary pump with orbiting rotor of harder material than stator
US3507585A (en) Rotary diaphragm pump
US5466137A (en) Roller gerotor device and pressure balancing arrangement therefor
EP0053868A2 (fr) Pompe à piston à mouvement gyratoire
US2688924A (en) Piston pump, in particular with eccentric drive
KR102368278B1 (ko) 편심 구동 베인을 구비한 진공 펌프 (편심 펌프 디자인)
US2915982A (en) Rotary pump
JPH0248753B2 (fr)
US2033218A (en) Rotary pump
US2132813A (en) Rotary engine
US3912427A (en) High pressure gear pump
US4265605A (en) Rotary pump with wedge roller eccentric means driving the rotor
JP2001027186A (ja) ベーンポンプ
US3694114A (en) Fluid flow machine with axially biassed rotor assembly
US5032069A (en) Rotary position displacement pump or motor
US3847519A (en) Gear pump arrangement
US3930766A (en) Radial balancing means for a hydraulic device
US5201647A (en) Rotary hydraulic vane device having a shaf seal
US2068570A (en) Rotary pump
US3884124A (en) Hydraulic device
US3119345A (en) End ported roller pump

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): CH DE FR GB IT NL

RBV Designated contracting states (corrected)

Designated state(s): CH DE FR GB IT LI NL

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): CH DE FR GB IT LI NL

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19840703