EP0149471A2 - Machine rotative à fluide du type à pallettes - Google Patents

Machine rotative à fluide du type à pallettes Download PDF

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Publication number
EP0149471A2
EP0149471A2 EP85100187A EP85100187A EP0149471A2 EP 0149471 A2 EP0149471 A2 EP 0149471A2 EP 85100187 A EP85100187 A EP 85100187A EP 85100187 A EP85100187 A EP 85100187A EP 0149471 A2 EP0149471 A2 EP 0149471A2
Authority
EP
European Patent Office
Prior art keywords
rotor
vane
shaft
vanes
fluid machine
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Withdrawn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
EP85100187A
Other languages
German (de)
English (en)
Other versions
EP0149471A3 (fr
Inventor
Isao Hayase
Yukio Takahashi
Masao Mizukami
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0149471A2 publication Critical patent/EP0149471A2/fr
Publication of EP0149471A3 publication Critical patent/EP0149471A3/fr
Withdrawn legal-status Critical Current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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 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

Definitions

  • the present invention relates to a rotary-vane type fluid machine wherein a rotor is caused to rotate within a casing to increase or decrease the volume of a space created between the outer periphery of the rotor and the inner wall surface of the casing by vanes caused to rotate jointly with the rotor, to thereby transfer fluid by pressure in accordance with the variation in volume of the space.
  • This type of fluid machine is well known, for example, as an internal combustion engine disclosed in the specification of the United States Patent No. 3, 121, 421, or as a fluid compressor disclosed in the specification of the United States Patent No. 2, 827, 226, or as a pump disclosed in the specification of the United States Patent No. 2, 816, 702.
  • a principal object of the invention is to provide a rotary-vane type fluid machine which enables a substantially zero clearance to be established between the tip end of the vane and the inner wall surface of the cylinder without pressing the vane against the latter.
  • Another object of the invention is to provide a rotary-vane type fluid machine which enables a force urging the vane radially outwardly of the rotor to be always kept constant.
  • the characterizing feature of the present invention lies in the provision of vane structures each of which two vanes are located substantially symmetrically with respect to a shaft intended to rotate the rotor and are fixed such that they can not move relative to each other, and in the provision of a crank mechanism which causes the vane structures to radially advance and retreat in order to reciprocally vary the distance between a center of the shaft and a tip end of one vane and the distance between the center of the shaft and a tip end of the other vane in accordance with the rotation of the rotor.
  • the characterizing feature of the present invention is directed to a rotary-vane type fluid machine which comprises
  • Fig. 1 is a front sectional view and Fig. 2 is a side sectional view thereof.
  • a reference numeral 1 denotes a rotor
  • a reference numeral 2 denotes a casing
  • reference numerals 3 and 4 denote side plates.
  • reference numerals 5 to 10 respectively denote a slider, a shaft, a tip seal, a vane, a side plate cover, and a shaft seal.
  • the rotor 1 is formed into a cylindrical shape and is formed with radially extending slits 16 at angular intervals of 90° in outer periphery.
  • the rotor 1 is also formed, at its central part of its axis, with a disc-shaped portion la which is formed, at its central part, with a boss portion lb.
  • a reference numeral lc is a space through which the vane 8 is moved.
  • the casing 2 is formed with a suction port 2a and a discharge port 2b. This discharge port 2b is attached with a discharge valve 11 and a discharge-valve keeper 12, which are covered by a cover 13 for the discharge chamber.
  • the rotor 1 is mounted by bearings 14 and 15 of the side plates 3 and 4 so that its outer periphery can be approached, at one place, to the inner wall surface of the casing 2.
  • the side plates 3, 4 are respectively formed with slider-carrying bosses 3a, 4a in such a manner that these bosses are made eccentric, by a distance of 6, from the center of the bearings 14, 15 as shown in Fig. 1, and in a direction spaced apart 180° from the position at which the rotor 1 approaches the inner wall surface of the cylinder 2 as shown in Figs. 2 and 3.
  • the slider-carrying bosses 3a, 4a constitute a part of a crank mechanism involved.
  • the slider 5, which constitutes a part of the crank mechanism, comprises, as shown in Fig. 5, a fitting hole 5a which is rotatably fitted onto the slider-carrying boss 3a or 4a and flat surfaces 19, 19 provided at two opposed outer peripheral positions in which a corresponding guided-by-slider portions 18 of vane structures 17 shown in detail in Fig. 6 are guided as the rotor 1 is rotated.
  • the flat surfaces 19 are provided, respectively, on four sides of the square slider 5 so as to guide two vane structures, or four vanes 8.
  • the vane structure 17 comprises a pair of such vanes 8, 8 which are disposed at its two opposed positions spaced 180° from each other as shown in Fig.
  • the connecting pieces 20 are intended to hold the vanes 8, 8 in the same plane and, in this embodiment, they are disposed in a manner that they are allowed substantially to oppose each other.
  • the connecting pieces 20 are provided, therebetween, with an elliptical hole 21 so that the vanes may be kept out of contact with the shaft when the shaft is inserted therebetween.
  • the vane structure 17 is substantially U-shaped in section and is provided with the vanes 8, 8 at the opposed portions of the U-shape, respectively.
  • the vane structure 17 is also provided with guided-by-slider portions 18, 18 at the foot portion of the U - shape where the vanes 8, 8 are connected by means of the connecting pieces 20, 20, said guided-by-slider portions 18, 18 being guided by the flat surfaces 19, 19 of the slider 5 as stated above.
  • the vane structure 17 is assembled into the rotor 1 and onto the sliders 5, 5 which are mounted onto the slider-carrying bosses 3a, 4a, the concaved portions of the two-U-shaped vane structures 17 are arranged to oppose each other in a state wherein one of the two is inclined at an angle of 90° with respect to the other, and in this state the vane structures 17 are assembled onto the sliders 5, 5.
  • This compressor is assembled as follows.
  • the casing 2 is fixed to the side plate 4 in a state wherein this side plate 4 is located at the lower side, and then the slider 5 is fitted onto the boss portion 4a of the side plate 4.
  • the rotor 1 to which the shaft 6 is fixed as shown in Fig. 3c is held in a posture wherein the shaft 1 is erected vertically.
  • the elliptical hole 21 of the vane structure 17 is fitted over the shaft 6 in a state wherein the A side shown in Fig. 6b is located at the lower side.
  • the vanes 8, 8 are inserted into the slits 16, 16 of the rotor 1 while, on the other hand, the guided-by-slider portions 18, 18 are fitted onto the flat surfaces 19, 19 of the slider 5.
  • the other vane structure 17 is assembled. Namely, the vane structure 17 is inclined at an angle of 90° with respect to the previous vane structure 17 and the A side shown in Fig. 6b is turned upside. In this state, similarly, the elliptical hole 21 is fitted over the shaft 6 and the vanes 8, 8 are inserted into the slits 16, 16. Then, the slider 5 is fitted into the guided-by-slider portions 18, 18 which are located upside of the vane structure 17. Thereafter, the slider-carrying boss portion 3a of the side plate 3 is fitted into the fitting hole 5a of the slider 5 and is fixed thereto.
  • the rotor 1 When the members are assembled in the above-mentioned manner, the rotor 1 is caused to rotate by the shaft 6, so that the vanes 8 are also caused to rotate. At this time, the guided-by-slider portions 18 of the vane structure 17 are caused to slide, in the directions indicated in Fig. 1 by arrows, on the flat surfaces 19 of the sliders 5 which rotate about the axis of the slider-carrying bosses 3a, 4a of the side plates 3, 4, whereby the compression action of the compressor is performed.
  • the compressor of Fig. 7 has only one vane structure 17 equipped with one pair of vanes 8.
  • the point 0 is a center of the rotor 1, i.e., an axial center of the shaft 6. Accordingly, the center line l1 of the vanes 8 inserted into two opposed slits 16 of the rotor 1 unavoidably passes through the point 0 regardless of the rotational angle 8 of the rotor 1.
  • the point A is a center of the slider-carrying bosses 3a, 4a of the side plates 3, 4.
  • the slider 5 is formed, at its outer periphery, with four parallel flat surfaces 19, 19 centering the point A.
  • the vane structure 17 is formed with the guided-by-slider portions 18, 18 extending in the direction perpendicular to center line l1.
  • the vane structure 17 is slidably fitted onto the two flat surfaces 19, 19 of the slider 5. Accordingly, a center line between the guided-by-slider portions 18, 18 of the vane structure 17, i.e., a perpendicular bisector k2 of the vane structure 17 unavoidably passes through a rotational center of the slider 5 regardless of the rotational angle 6 of the rotor 1, or the point A.
  • the angle ⁇ OBA which is formed by connecting the two fixed points 0 and A spaced by a distance of 6 from each other with the intersection B of the center line l1 of the vane structure 17 and the perpendicular bisector l2 of the vane structure 17, is 90°.
  • the point B (the center of gravity of the vane structure 17) is located on the circumference of a circle of which center is a middle point C between the points O and A and the radius is 6/2, regardless of the rotational angle 6 of the rotor 1. Further, since the angle ⁇ BCA which is formed by the lines CB and CA and the angle ⁇ B O A which is formed by the lines OB and OA have a relation of the central angle and the angle of circumference with respect to the common circular arc AB, the following relationship is formed.
  • the distance OB between the center 0 of the rotor 1 and the center B of gravity of the vane structure 17 is expressed as follows. This indicates that the vane structure 17 reciprocates within the slits 16 of the rotor 1 with a stroke of 26 and a cycle of which one rotation of the rotor 1 is one cycle.
  • each of opposite outer ends of the vanes 8 is made an arc of a circle having a radius of r and the distance between the center B of gravity and the center D of E of . such arc is so set as to have the following value.
  • the loci which are described by the centers D and E of the curved surfaces R of the outer ends of the vanes 8 are expressed in the form of a polar coordinate as follows.
  • the curve which is expressed by the above formula (3) is indicated in Fig. 7 as a closed curve Cl.
  • the locus which is described by the curved surface R of the outer end of the vane 8 is an envelope C2 formed when the circles whose radius is r are arranged on the closed curve Cl.
  • a closed curve C3 which is outwardly displaced by a fixed amount of Ar from the closed curve C2 is used as the profile of the inner wall surface of the casing 2.
  • the gap Ar created between the tip end of the vane 8 and the inner wall surface of the casing 2 is sealed by the tip seal 7.
  • a curve (such as, for example, a true circle approximate to the closed curve C3) other than the closed curve C3 may be used as the profile of the inner wall surface of the casing 2.
  • the gap between the tip end of the vane 8 and the inner wall surface of the cylinder 2 is periodically slightly varied with the rotation of the rotor 1.
  • the tip seal 7 can be more or less advanced or retreated within a groove 8a at the tip end of the vane 8 in accordance with the variation in said gap, it will be possible to effect an always perfect sealing with respect to the gap.
  • the space discharges fluid from the discharge port 2b and, in (c) and (d) of Fig. 8, it sucks fluid from the suction port 2a.
  • the space compresses fluid in the stages of (g) and (h) of Fig. 8 and, in (a) of Fig. 8, starts discharging fluid.
  • the space is repeatedly decreased and increased in volume, thereby repeatedly to discharge and suction fluid, thus to perform its compression action as the compressor.
  • the vanes 8 are arranged to project at four places from the outer periphery of the rotor 1, four suctions and discharges are effected per rotation of the rotor 1.
  • the vanes are mechanically brought into sliding contact with the inner wall surface of the casing unlike the fluid machine of prior art in which the former are brought into sliding contact with the latter by use of back pressure. Therefore, it is impossible that the vanes are radially inwardly retreated with an increase in pressure of the compression chamber and that, therefore, the chattering phenomena take place. Further, since it is unnecessary to apply the back pressure, it is also unnecessary to separate oil used to apply the back pressure in a high pressure chamber. Accordingly, the space which is intended to be used for oil separation as well as for oil reception becomes unnecessary. As a result, it becomes possible to reduce the fluid machine in size as well as in weight.
  • the fluid machine of this embodiment is high in durability as well as in working efficiency.
  • two connecting pieces were used for connecting the vanes 8 in such a manner that they form an elliptic hole therebetween.
  • a single connecting piece may be used to connect the pair of vanes 8.
  • two sliders are used, but the invention permits the use of only one slider.
  • the disc-shaped portion having the boss portion is provided at the central part of the rotor 1, but the invention permits the formation of it at the end portion thereof.
  • the tip seal 7 was provided at the tip end of the vane. However, when the fluid machine is used as a pump, this tip seal 7 may be omitted. In this case, the discharge valve 11 which is provided with respect to the discharge port 2b may be omitted.
  • the back surface of the tip seal may be urged by means of a spring.
  • the spring may be a one which has an urging force much weaker than that of a spring used to urge the entire vane as in the prior art. Accordingly, the mechanical loss resulting from the sliding contact between the tip seal and the inner wall surface of the cylinder is decreased to a substantially ignorable value.
  • the tip seal 7 is formed with a shoulder portion 7d in addition to merely urging by means of a spring 7a, which shoulder portion 7d is caused to oppose a shoulder portion 7c of a tip-seal insertion hole 7b.
  • This construction offers the advantage that when the tip seal 7 is worn and as a result the shoulder portions 7d and 7c are allowed to contact with each other, the tip seal 7 is prevented from being further extruded outwards, with the result that a zero clearance is provided between the tip seal 7 and the inner wall surface of the cylinder.
  • a pair of vanes are disposed within one plane which passes through the center of the shaft, but the vanes may define a specified angle with respect to this plane, or may be disposed symmetrically about the center of the shaft.
  • the vanes are so arranged as to be radially advanced and retreated by means of a crank mechanism, it is impossible that the tip ends of the vanes are pressed against the inner wall surface of the cylinder. Accordingly, it is possible to make substantially zero clearance between the tip ends of the vanes and the inner wall surface of the cylinder.
  • vanes By arranging the vanes as above, it is possible to decrease the mechanical loss which results from the sliding contact between the tip ends of the vanes and the inner wall surface of the cylinder, thereby to make it possible to obtain a highly efficient fluid machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP85100187A 1984-01-11 1985-01-10 Machine rotative à fluide du type à pallettes Withdrawn EP0149471A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP3304/84 1984-01-11
JP59003304A JPS60147591A (ja) 1984-01-11 1984-01-11 流体機械

Publications (2)

Publication Number Publication Date
EP0149471A2 true EP0149471A2 (fr) 1985-07-24
EP0149471A3 EP0149471A3 (fr) 1987-04-08

Family

ID=11553615

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85100187A Withdrawn EP0149471A3 (fr) 1984-01-11 1985-01-10 Machine rotative à fluide du type à pallettes

Country Status (3)

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EP (1) EP0149471A3 (fr)
JP (1) JPS60147591A (fr)
KR (1) KR850005577A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000049295A1 (fr) * 1997-10-06 2000-08-24 Svensson Goesta Compresseur rotatif a palettes
WO2007054162A1 (fr) * 2005-11-14 2007-05-18 Joma-Hydromechanic Gmbh Pompe a rotor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6036462A (en) * 1997-07-02 2000-03-14 Mallen Research Ltd. Partnership Rotary-linear vane guidance in a rotary vane machine
KR102581585B1 (ko) * 2019-04-09 2023-10-05 허일행 편심축을 이용한 유체 펌프 및 모터

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE72347C (de) * E. B. DONKIN in Southwark Park Road, Bermondsey, County of Surrey, England Kapselwerk mit die Wirkung ausgleichendem Regelungskolben
DE401297C (de) * 1921-12-07 1924-09-01 Joseph Baudot Maschine mit umlaufenden Kolben, die durch eine besondere Gleitfuehrung von der Welle aus gefuehrt werden
FR597560A (fr) * 1925-11-24
US1940384A (en) * 1927-05-07 1933-12-19 Zoller Arnold Rotary compressor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE785646A (fr) * 1972-06-29 1972-10-16 Chevalier Victor Pompe rotative a debit variable,
JPS5122201A (ja) * 1974-08-17 1976-02-21 Takeshi Nakagawa Kuroorashikifuookukenyoshoberu
JPS5768577A (en) * 1980-10-16 1982-04-26 Nippon Soken Inc Rotary pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE72347C (de) * E. B. DONKIN in Southwark Park Road, Bermondsey, County of Surrey, England Kapselwerk mit die Wirkung ausgleichendem Regelungskolben
FR597560A (fr) * 1925-11-24
DE401297C (de) * 1921-12-07 1924-09-01 Joseph Baudot Maschine mit umlaufenden Kolben, die durch eine besondere Gleitfuehrung von der Welle aus gefuehrt werden
US1940384A (en) * 1927-05-07 1933-12-19 Zoller Arnold Rotary compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000049295A1 (fr) * 1997-10-06 2000-08-24 Svensson Goesta Compresseur rotatif a palettes
WO2007054162A1 (fr) * 2005-11-14 2007-05-18 Joma-Hydromechanic Gmbh Pompe a rotor

Also Published As

Publication number Publication date
KR850005577A (ko) 1985-08-28
JPS60147591A (ja) 1985-08-03
EP0149471A3 (fr) 1987-04-08
JPH0313435B2 (fr) 1991-02-22

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