US3598510A - Vane pump - Google Patents

Vane pump Download PDF

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Publication number
US3598510A
US3598510A US13376A US3598510DA US3598510A US 3598510 A US3598510 A US 3598510A US 13376 A US13376 A US 13376A US 3598510D A US3598510D A US 3598510DA US 3598510 A US3598510 A US 3598510A
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United States
Prior art keywords
vane
axial
cam ring
passage
pair
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US13376A
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English (en)
Inventor
Yasuo Aoki
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Komatsu Ltd
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Komatsu Ltd
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Filing date
Publication date
Application filed by Komatsu Ltd filed Critical Komatsu Ltd
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Publication of US3598510A publication Critical patent/US3598510A/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • This invention relates to improvements in a vane pump comprising a housing having an inlet and an outlet, a cam ring, and a rotor, in which the rotor is adapted to be rotated inside the cam ring and slid on two inner sidewalls of the housing and has a plurality of axial through-passages, which are radially outwardly extended into vane-guiding slots, in which vanes are adapted to be radially slidable, respectively.
  • vanes are pushed against the inner circumferential wall of the cam ring for securing a high watertightness. It is also well known that a hydraulic pressure in the outlet is introduced into the axial through-passages for pushing the vanes which are radially outwardly slidable in vaneguiding slots extended from the axial through-passages.
  • the primary object of this invention is to provide a vane pump of the class described, in which the variation in balancing the two pressures is minimized.
  • Another object of this invention is to provide a vane pump of the class described, of which the pumpability is remarkably improved.
  • Still another object of this invention is to provide a vane pump of the class described, which is well prevented from generation of vibration and noise.
  • a vane pump comprising a housing having at least a pair of an inlet and an outlet, a cam ring, and a rotor, the rotor being adapted to be rotated inside the cam ring and slid on two inner walls of the housing and having a plurality of axial through-passages, which are radially outwardly extended into vane-guiding slots, in which vanes are adapted to be radially slidable, respectively.
  • the vane is adapted to be radially outwardly pressured by liquid introduced into the axial through-passages from the outlet and radially inwardly pressure by an inner circumferential wall of the cam ring.
  • An annular groove is formed in one of the two inner sidewalls, arranged in such a position as to always communicate with the outlet and with an end of the axial throughpassages, and provided with throttles positioned on the same radii with both circumferential ends of the inlet.
  • a segmental groove is formed in the other of the two inner sidewalls, arranged in such a position as to communicate with the inlet intermediate still another throttle and with the other end of the axial thorugh-passages, and circumferentially extended between points radially corresponding to the both circumferential ends of the inlet.
  • the vane may be provided with a plurality of radial slits formed in the forward surface thereof. the slits being extended from the radially inner end thereof to points positioned somewhat radially outer than the periphery of the rotor when the vane is radially most outwardly positioned while being in contact with the cam ring.
  • FIG. 1 is an axially sectional view of a vane pump embodying this invention
  • FIG. 2 is a partly removed cross-sectional view thereof taken along the line 2-2 in FIG. I;
  • FIG. 3 is another partly removed cross-sectional view thereof taken along the line 3-3 in FIG. 1;
  • FIG. 4 is an enlarged front view of a vane
  • FIG. 5 is a side elevational view thereof
  • FIG. 6 is an explanatory view of the exhausting stroke, in which the cross sections of a vane and arrangement of the annular groove are shown;
  • FIG. 7 is an explanatory view of the sucking stroke, in which the cross sections of a vane and arrangement of the segmental groove are shown.
  • FIG. 8 shows the interrelation of pressure to the arrangement of the annular groove, the segmental groove, and the slit.
  • a housing 11 having a cavity having an inlet 16 and an outlet 17.
  • a pressure plate 19 and a wear plate 20 are arranged in opposition to each other in the cavity.
  • a cam ring 12 is arranged between the pressure plate 19 and the wear plate 20 in the cavity.
  • An inner periphery of the cam ring 12 constitutes a pumping chamber together with opposite inner sidewalls of the pressure plate 19 and the wear plate 20.
  • the contour of the inner periphery of the cam ring 12 resembles an ellipse, but actually it is formed with a pair of larger circular parts. a pair of smaller circular parts, and two pairs of cam curve parts, each connecting the larger circular part with the smaller circular part, so that this vane pump is of two strokes, as shown in FIGS. 2 and 3.
  • a rotor 13 is arranged inside the pumping chamber. Both plane surfaces of the rotor 13 are adapted to be slid on the plane surfaces of the inner walls of the pressure plate 19 and the wear plate 20, respectively.
  • the rotor 13 is provided with a plurality of axial through-passages 34 arranged on a coaxial cylinder, which are radially outwardly extended into vaneguiding slots 14, respectively.
  • a vane 15 is adapted to be radially slidable in the vane-guiding slot 14 and to be circumferentially travelled in accordance with the contour of the inner periphery of the cam ring 12 when the rotor 13 is externally rotated as in the prior art.
  • the inlet 16 is divided into two sucking ports 116 and 216 formed through the pressure plate 19 and the wear plate 20 so as to communicate the inlet 16 with the pumping chamber as shown in FIGS. 2 and 3.
  • the outlet 17 is divided into two exhausting ports 117 and 217 formed through the pressure plate 19 so as to communicate the outlet 17 with the pumping chamber as shown in FIG. 2.
  • the pressure plate 19 is provided with an annular groove 18 formed in the inner sidewall thereof and arrange in such a position as to be always communicate with the outlet 17 through a pair of passages 22 and the exhausting ports 117 and 217 and with an end of the axial through-passage 34.
  • the annular groove 18 is provided with a pair of first throttles 41 and a pair of second throttles 42, of which the positions are referred to in detail hereinafter.
  • the wear plate 20 is provided with a pair of segmental grooves 21 formed in the inner sidewall thereof and arranged in such a position as to communicate with the inlet 16 through a pair ofthird throttles 45 and the sucking ports 116 and 216 and with the other end of the axial through-passage 34.
  • the segmental groove 21 is circumfcrentially extended from a point 46 axially corresponding to the first throttle 41 to another point 47 axially corresponding to the second throttle 42, as shown in FIGS. 3, 7 and 8.
  • the vane 15 is provided with a plurality of radial slits 24 formed in the forward surface thereof.
  • the radial slit 24 is extended from the radially inner end of the vane 15 to a point 48 positioned radially outer than the periphery of the rotor 13 when the vane 15 is radially most outwardly positioned or in contact with the larger circular part ofthe cam ring 12.
  • FIG. 8 showing the interrelation of pressure to the construction.
  • the ordinate represents the differential pressure subjected to the unit area of the vane 15, while the abscissa represents time of the travelling vane.
  • arrangements of the annular groove 18 and the segment groove 21 are shown relatively to positions of a vane 15, in which the annular groove 18 and the segmental groove 21 are deformed into rectilinear ones.
  • the annular groove 18 comprises two pairs of throttles 41 and 42 as stated hereinbefore, which divide the annular groove 18 into a pair of longer parts 118 and a pair of shorter parts 218.
  • the outlet 17 is communicated with the pair of exhausting ports 117 and 217, each of which is communicated with the longer part 118 intermediate the passage 22.
  • the longer part 118 is communicated with a shorter part 218 intermediate the two throttles 41 and 42, so that, during the axial through-passage 34 is communicated with the longer part 118, the pressure of the liquid in the axial throughpassage 34 introduced from the outlet 17 is higher than that during the axial through-passage is communicated with the shorter part 218 by virtue of the throttles 41 and 42.
  • the outer end of the vane 15 travels along a larger circular part, is pushed inwardly by a cam curve part, and again travels along a smaller circular part.
  • the axial through-passage 34 is communicated with the shorter part 218 from the first throttle 41 to the second throttle 42, the outer end of the vane 15 protrudes outwardly and travels along another cam curve part of the inner periphery of the cam ring 12, by which the protruded outer end is retained.
  • this period it is required to avoid a too high pressure subjected to the inner end of the vane 15, balancing with the low pressure subjected to the outer end of 'the vane 15, which becomes as low as kg./cm
  • the segmental groove 21 is positioned axially correspondingly to the shorter part 216 of the annular groove 18 and communicated with the sucking port of the inlet 16 through the third throttle 45.
  • An excessive liquid in the axial through-passage 34 which causes the too high pressure, is delivered to the segmental groove 21, whence the liquid is returned to the sucking port 116 and 216 through the third throttle 45.
  • FIG. 6 the cam curve part of the inner periphery of the cam ring 12 and the annular groove 18 are shown as deformed into straight lines. It is to be understood that one of the vanes 15 and one of the axial through-passages 34 are travelling from left to right through three positions, D, E, and F. Although the outer end of the vane 15 is in contact with the larger circular part of the cam ring 12 at the position D, the outer end is subsequently pushed inwardly by the cam curve part of the cam ring 12 successively at the positions E and then F.
  • the axial through-passage 34 is communicated with the longer part 118 of the annular groove 18 so that the inner end of the vane 15 is directly affected by the high pressure of the liquid in the outlet 17 which balances with the inward pushing action rendered by the cam curve part.
  • FIG. 7 another cam curve part of the inner periphery of the cam ring 12 and the segmental groove 21 are shown as deformed into straight lines.
  • one of the vanes 15 and one of the axial through-passages 34 are travelling from left to right through three positions, A, B, and C.
  • the cam curve part of the cam ring 12 is gotten away from the rotor 13 as the rotor rotates and in accordance therewith the vane 15 is outwardly protruded as it travels from the position A to the position B.
  • the axial throughpassage 34 passes the end point 47 of the segmental groove 21 and is disengaged from the latter so that the communication of the axial through-passage 34 with the segmental groove 21 is interrupted between the positions B and C.
  • the vane 15 is protruded outwardly to the point 48 out of the periphery 49 of the rotor 13 so that the outer end of the radial slits 24 is exposed in the pumping chamber and the axial through-passage 34 is communicated with the pumping chamber through the radial slits 24, and therefore the high pressure in the axial through-passage 34 is leaked from it to the pumping chamber little by little so as to relieve the pressure subjected to the vane 15.
  • a variation in the differential pressure acting on the vane 15 is shown by a full line, which represents a case where the segmental groove 21 is provided but the radial slits 24 are not.
  • the full line stepped at the position corresponding to the end 47 of the segmental groove 21 is smoothed as shown by a broken line.
  • the differential pressure acting on the vane 15 for protruding it is made about constant throughout the entire round travelling course of the vane 15, not concerning with variation in pressure in the pumping chamber.
  • the positions of the throttles 41 and 42, the degree of throttling thereof, and the number, form and length of the radial slits 24 may be selected depending upon the characteristics of a pump.
  • a vane pump comprising a housing having at least a pair of inlets and a pair of outlets, a cam ring, and a rotor
  • said rotor being adapted to be rotated inside said cam ring and slidable on two inner sidewalls of the housing and having a plurality of axial through-passages, each axial through-passage being radially outwardly extended into a vane-guiding slot, in which a vane is adapted to be radially slidable, said vane being adapted to be radially outwardly pressured by liquid introduced into said axial through-passage from said outlets, and radially inwardly pressured by an inner circumferential wall of said cam ring, an annular groove formed in one of said two inner sidewalls, arranged in such a position as to always communicate with said outlets and with an end of said axial throughpassage, and provided with two throttles positioned on the same radii with both circumferential ends of each inlet, respectively, and
  • segmental grooves formed in the other of said two inner sidewalls each segmental groove arranged in such a position as to communicate with each inlet through still another throttle and with the other end of said axial through-passage, and circumferentially extended between two points corresponding to said both circumferential ends of each inlet.
  • said slit being extended from the radially inner end thereof to a point positioned radially outwardly of the periphery of said rotor when said vane is in contact with said ring and said segmental groove is disengaged from said axial through-passage.
  • contour of the inner periphery of said cam ring comprises a pair of larger circular parts, a pair of smaller cir cular parts, and two pairs of cam curve parts, each connecting the larger circular part with the smaller circular part, so that the vane pump is of two strokes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US13376A 1969-02-27 1970-02-24 Vane pump Expired - Lifetime US3598510A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP44014874A JPS5031643B1 (enrdf_load_stackoverflow) 1969-02-27 1969-02-27

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US3598510A true US3598510A (en) 1971-08-10

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US13376A Expired - Lifetime US3598510A (en) 1969-02-27 1970-02-24 Vane pump

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JP (1) JPS5031643B1 (enrdf_load_stackoverflow)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2157637A1 (de) * 1971-11-20 1973-05-24 Rexroth Gmbh G L Fluegelzellenpumpe oder -motor
US3828569A (en) * 1973-07-11 1974-08-13 Gen Motors Corp Automotive air conditioning system
US3973881A (en) * 1974-02-06 1976-08-10 Daimler-Benz Aktiengesellschaft Vane-type pump or motor with undervane fluid bias
US4104010A (en) * 1975-08-18 1978-08-01 Diesel Kiki Co. Ltd. Rotary compressor comprising improved rotor lubrication system
EP0057309A3 (en) * 1981-02-02 1982-09-01 Abex Corporation Sliding vane motor with vane biasing means
FR2504608A1 (fr) * 1981-04-23 1982-10-29 Gen Motors Corp Pompe a palettes equilibree en pression et a amorcage automatique
US4455129A (en) * 1981-05-19 1984-06-19 Daikin Kogyo Co., Ltd. Multi-vane type compressor
FR2568952A1 (fr) * 1984-04-09 1986-02-14 Barmag Barmer Maschf Pompe multicellulaire a palettes
US4604041A (en) * 1984-04-09 1986-08-05 Barmag Barmer Maschinenfabrik Aktiengesellschaft Rotary vane pump
US4717321A (en) * 1982-06-18 1988-01-05 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US5154593A (en) * 1990-03-09 1992-10-13 Jidosha Kiki Co., Ltd. Vane pump with annular groove in rotor which connects undervane chambers
US5266018A (en) * 1992-07-27 1993-11-30 Vickers, Incorporated Hydraulic vane pump with enhanced axial pressure balance and flow characteristics
US5490770A (en) * 1993-11-26 1996-02-13 Aisin Seiki Kabushiki Kaisha Vane pump having vane pressurizing grooves
US5947712A (en) * 1997-04-11 1999-09-07 Thermo King Corporation High efficiency rotary vane motor
US6027323A (en) * 1997-01-29 2000-02-22 Danfoss A/S Hydraulic vane machine
WO2002027187A3 (en) * 2000-09-28 2002-06-20 Coltec Ind Inc Vane pump
WO2002027188A3 (en) * 2000-09-28 2002-06-20 Coltec Ind Inc Vane pump
US6663357B2 (en) 2000-09-28 2003-12-16 Goodrich Pump And Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US20040131477A1 (en) * 2000-09-28 2004-07-08 Dalton William H. Vane pump wear sensor for predicted failure mode
US8540500B1 (en) 2012-05-08 2013-09-24 Carl E. Balkus, Jr. High capacity lightweight compact vane motor or pump system
US20140030130A1 (en) * 2010-12-01 2014-01-30 Xylem Ip Holdings Llc Sliding vane pump
US20170184102A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device
US20170184104A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device
US20170184105A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3255704A (en) * 1965-02-24 1966-06-14 New York Air Brake Co Pump
US3329067A (en) * 1964-11-23 1967-07-04 Nils O Rosaen Fluid motors

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3329067A (en) * 1964-11-23 1967-07-04 Nils O Rosaen Fluid motors
US3255704A (en) * 1965-02-24 1966-06-14 New York Air Brake Co Pump

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2157637A1 (de) * 1971-11-20 1973-05-24 Rexroth Gmbh G L Fluegelzellenpumpe oder -motor
US3813194A (en) * 1971-11-20 1974-05-28 Rexroth Gmbh G L Hydraulic vane machine with controlled vanes
US3828569A (en) * 1973-07-11 1974-08-13 Gen Motors Corp Automotive air conditioning system
US3973881A (en) * 1974-02-06 1976-08-10 Daimler-Benz Aktiengesellschaft Vane-type pump or motor with undervane fluid bias
US4104010A (en) * 1975-08-18 1978-08-01 Diesel Kiki Co. Ltd. Rotary compressor comprising improved rotor lubrication system
EP0057309A3 (en) * 1981-02-02 1982-09-01 Abex Corporation Sliding vane motor with vane biasing means
US4386891A (en) * 1981-04-23 1983-06-07 General Motors Corporation Rotary hydraulic vane pump with undervane passages for priming
DE3212363A1 (de) * 1981-04-23 1983-02-10 General Motors Corp., Detroit, Mich. Selbstanlaufende fluegelkolbenpumpe
FR2504608A1 (fr) * 1981-04-23 1982-10-29 Gen Motors Corp Pompe a palettes equilibree en pression et a amorcage automatique
US4455129A (en) * 1981-05-19 1984-06-19 Daikin Kogyo Co., Ltd. Multi-vane type compressor
US4717321A (en) * 1982-06-18 1988-01-05 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
FR2568952A1 (fr) * 1984-04-09 1986-02-14 Barmag Barmer Maschf Pompe multicellulaire a palettes
US4604041A (en) * 1984-04-09 1986-08-05 Barmag Barmer Maschinenfabrik Aktiengesellschaft Rotary vane pump
US5154593A (en) * 1990-03-09 1992-10-13 Jidosha Kiki Co., Ltd. Vane pump with annular groove in rotor which connects undervane chambers
US5266018A (en) * 1992-07-27 1993-11-30 Vickers, Incorporated Hydraulic vane pump with enhanced axial pressure balance and flow characteristics
US5490770A (en) * 1993-11-26 1996-02-13 Aisin Seiki Kabushiki Kaisha Vane pump having vane pressurizing grooves
US6027323A (en) * 1997-01-29 2000-02-22 Danfoss A/S Hydraulic vane machine
US5947712A (en) * 1997-04-11 1999-09-07 Thermo King Corporation High efficiency rotary vane motor
US7207785B2 (en) 2000-09-28 2007-04-24 Goodrich Pump & Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
WO2002027188A3 (en) * 2000-09-28 2002-06-20 Coltec Ind Inc Vane pump
US6634865B2 (en) 2000-09-28 2003-10-21 Goodrich Pump And Engine Control Systems, Inc. Vane pump with undervane feed
US6663357B2 (en) 2000-09-28 2003-12-16 Goodrich Pump And Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US20040047741A1 (en) * 2000-09-28 2004-03-11 Dalton William H. Vane pump with undervane feed
US20040131477A1 (en) * 2000-09-28 2004-07-08 Dalton William H. Vane pump wear sensor for predicted failure mode
US7083394B2 (en) 2000-09-28 2006-08-01 Goodrich Pump & Engine Control Systems, Inc. Vane pump with undervane feed
WO2002027187A3 (en) * 2000-09-28 2002-06-20 Coltec Ind Inc Vane pump
US9556870B2 (en) * 2010-12-01 2017-01-31 Xylem Ip Holdings Llc Sliding vane pump
US20140030130A1 (en) * 2010-12-01 2014-01-30 Xylem Ip Holdings Llc Sliding vane pump
GB2486007B (en) * 2010-12-01 2017-05-10 Itt Mfg Enterprises Inc Sliding vane pump
US8540500B1 (en) 2012-05-08 2013-09-24 Carl E. Balkus, Jr. High capacity lightweight compact vane motor or pump system
US20170184102A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device
US20170184104A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device
US20170184105A1 (en) * 2015-12-25 2017-06-29 Showa Corporation Vane pump device
US10443598B2 (en) * 2015-12-25 2019-10-15 Showa Corporation Vane pump device for controlling force applied to vanes
US10584703B2 (en) * 2015-12-25 2020-03-10 Showa Corporation Vane pump device for controlling fluid supplied to vane grooves
US10655624B2 (en) * 2015-12-25 2020-05-19 Showa Corporation Vane pump device for controlling deviation of a force applied to the vanes

Also Published As

Publication number Publication date
JPS5031643B1 (enrdf_load_stackoverflow) 1975-10-14

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