WO1999004167A1 - Pompe a palettes - Google Patents

Pompe a palettes Download PDF

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Publication number
WO1999004167A1
WO1999004167A1 PCT/KR1998/000213 KR9800213W WO9904167A1 WO 1999004167 A1 WO1999004167 A1 WO 1999004167A1 KR 9800213 W KR9800213 W KR 9800213W WO 9904167 A1 WO9904167 A1 WO 9904167A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
vane
air
circular
space
Prior art date
Application number
PCT/KR1998/000213
Other languages
English (en)
Japanese (ja)
Inventor
Dong Il Hwang
Vin Hwang
Original Assignee
Dong Il Hwang
Vin Hwang
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
Priority claimed from KR1019970033359A external-priority patent/KR100231475B1/ko
Priority claimed from KR1019970045563A external-priority patent/KR100254171B1/ko
Priority claimed from KR1019970050116A external-priority patent/KR19990027626A/ko
Application filed by Dong Il Hwang, Vin Hwang filed Critical Dong Il Hwang
Priority to AU84640/98A priority Critical patent/AU8464098A/en
Publication of WO1999004167A1 publication Critical patent/WO1999004167A1/fr

Links

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
    • F04C18/40—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 having a hinged member
    • F04C18/44—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 having a hinged member with vanes hinged to the inner member
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the present invention relates to a vane pump.
  • the circular part of the internal rotor has the circular part on one side.
  • the present invention relates to a vane pump that prevents noise from being generated due to a collision while compressing air in a compression chamber between an inserted vane and an inner wall of an outer rotor.
  • a vane pump is a plurality of vanes that are provided so that at least one vane reciprocates while receiving elasticity by a spring on a rotor that is eccentrically rotated by a cylindrical cylinder and receives an elastic force outward in accordance with the rotation of the rotor. Oil flowing through the suction port while the vane is in contact with the inner peripheral edge of the cylinder, or It is widely known that a fluid such as air is compressed and discharged through a discharge port.
  • the distance between the rotor that rotates about the eccentric rotation axis inside the cylinder and the cylinder is varied while approaching or distant.
  • the rotor is configured to be protruded to the outside by the elastic force of the spring or to be pushed inward while being in contact with the inner wall of the cylinder. It has the disadvantage that it can be damaged due to damage, and the high speed of rotation cannot be achieved, and the material and size of the vane are limited.
  • the applicant has proposed a vane pump in Korean Patent Application No. 199 95 — 42007, which has a helical shaft cavity 2 formed at the center and is rotated by a motor (not shown).
  • the upper and lower air circulation holes 4 and 5 and the inflow air 6 and 7 penetrating through the side face are integrally formed on the outer peripheral surface of the outer rotor 1 with the inner rotor 3 integrally formed on both sides.
  • the outer rotor 11 which is formed so as to protrude in the longitudinal direction from the inflow spaces 6, 7 of the inner rotor 3, and is positioned so as to be eccentric with respect to the bearing portion 1 by being sandwiched between the cylindrical working spaces. Air is supplied to the air circulation holes 4 and 5 through a large axial cavity 12;
  • the closed space formed by the outer surface of the inner rotor 3 and the inner surface of the outer rotor 11 is divided into a compression chamber and a supply chamber on the right and left sides of the vane, and the volume of the compression chamber and the supply chamber varies.
  • the air compressed in the compression chamber is discharged to the outside through the discharge port of the external rotor 11
  • Air is supplied to a large axial space 12 of the external rotor 11 through an air supply path 22, 23 connected to the outside to a housing 21 in which a closed type compressed air storage chamber is formed between the external rotor 11 and the housing 21.
  • An oil circulation groove 28 is provided at a portion of the housing 21 having a small shaft space 25, which is in contact with the oil supply spaces 8 and 9 of the bearing portion 1 and in which the oil immersion portions 26 and 27 are formed in a circumferential shape and which is in contact with the external rotor 11 of the housing 21. And an oil circulation air 15 is formed in a large axial space 12 of the external rotor 11 which is in contact with the bearing 1.
  • the present invention solves the above-mentioned problems, and a vane having one side inserted into a circular hollow of an internal rotor that receives a rotational force through a center eccentric shaft through a transmission section of constant speed rotation.
  • the objective is to obtain high-pressure compressed air without generating noise during compression while the other side is in contact with the inner surface of the outer rotor.
  • noise is generated at the time of compression while the inner rotor rotates together with the inside of the outer rotor while the other side of the vane having one side inserted into the circular hollow of the inner rotor contacts the operating groove of the outer rotor.
  • Another object of the present invention is to obtain high-pressure compressed air.
  • the present invention provides a vane sandwiched through an opening on one side of a clamp inserted into a circular hollow of an internal rotor so that an external rotor rotates at a constant speed, so that noise is not generated during compression. Another object is to obtain high-pressure compressed air.
  • the present invention provides a method in which a thin clamp is inserted into a circular hollow of an inner rotor three times so that an outer rotor rotates at a constant speed in a state where a vane is sandwiched, so that noise is not generated during compression. Another object is to obtain high-pressure compressed air with stable operation.
  • the present invention for achieving the above-mentioned object is to form a ring gear in a space portion of a central bearing portion that receives a rotational force from the outside,
  • a ring gear formed in a space portion of the internal rotor is meshed with a linear gear on the other side of the constant velocity pulling in which one line gear is meshed with the ring gear so as to rotate at a constant speed.
  • a circular portion formed on the side of the vane is inserted into the circular cavity of the internal port
  • the other side of the vane compresses air in accordance with a state where the volumes of the compression chamber and the supply chamber are changed while being in contact with the inner surface of the outer rotor, so that noise due to collision does not occur, and both have a simple configuration. It is designed to obtain high-pressure compressed air with a small volume.
  • FIGS. 2 and 3 are views showing a configuration according to one embodiment of the present invention.
  • a ring gear 33 is provided in a space 32 on one side of a central bearing 31 which receives a rotational force from the outside through a motor (not shown). Formed in one piece,
  • a linear gear 36 is integrally formed and rotates at a constant speed even in an eccentric state.
  • the ring gear 39 of the space 38 is meshed with the line gear 36 on the other side of the constant-speed pulling ring 34 and receives a constant-speed rotating force.
  • the other inclined protrusion 44 on the other side of the vane 42 in which one circular portion 43 is sandwiched between the circular cavities 40 is in contact with the inner surface of the outer rotor 45 or is located in the insertion groove 41, and the inner rotor
  • the bearing cover 46 depends on the state in which the volumes of the compression chamber A and the supply chamber B change while being eccentrically rotated together with the external port 45 while one side of the van 42 is sandwiched by the circular cavity 40 of 37.
  • the air supplied to the compression chamber A through the air supply air 47 is compressed,
  • a compressed air storage chamber 49 is formed between the outer surface of the outer rotor 45 and the housing 48 to maintain a pressure equal to or higher than a predetermined pressure discharged through a discharge air 50 provided with a check valve 51 for preventing backflow of the outer rotor 45. After the compressed air is temporarily stored, it is discharged to an external tank.
  • the air flowing through the air supply air 47 of the bearing cover 46 is After being supplied to the supply chamber B defined by the vane 42 in which the circular portion 43 is inserted into the circular cavity 40 of 7 and the external rotor 45, the inclined protruding portion 44 of the vane 42 in contact with the internal rotor 37 and the external rotor 45 The compression is performed in the compression chamber A whose volume changes.
  • the air enters the supply chamber B, and the rotational force is transmitted and received through the constant-speed coupling 34 according to the rotation of the bearing portion 31, and the circular space 40 of the internal rotor 37 is circular. Since the inner rotor 37 and the outer rotor 45 are in airtight contact with the vane 42 between which the part 43 is sandwiched, the vane 42 on the other side moves rightward with the inclined projection 44 on the other side positioned in the insertion groove 41 of the circular cavity 40 of the inner rotor 37. To rotate.
  • the vane 42 in which the circular portion 43 is inserted into the circular space 40 of the internal rotor 37 by the bearing portion 31 moves 90 to the right together with the internal rotor 37 and the external rotor 45.
  • the volume of the compression chamber A, which was the supply chamber B was closed by the outer rotor 45, the inclined protrusion 44 of the vane 42, and the inner rotor 37, and the supply chamber B was newly secured. Air is introduced from outside.
  • the outer rotor 45 is more than the inner rotor 37 with the inclined protrusion 44 of the vane 42 in a state where the circular portion 43 is inserted into the circular cavity 40 of the inner rotor 37 being in contact with the inner surface of the outer rotor 45.
  • the circular portion 43 of the vane 42 slightly rotates in the circular space 40 of the internal rotor 37, so that the inclined protruding portion 44 of the vane 42 passes through the internal surface and the inclined surface of the external rotor 45.
  • the state of surface contact is maintained, and at this time, the inclined protrusion 44 of the vane 42 is stabilized by the pressure of the compressed air and the pressure of the newly introduced air flowing into the supply chamber B. Keep airtight Will be maintained.
  • the vane 42 in which the circular portion 43 is inserted into the circular cavity 40 of the inner rotor 37 is rotated more than the outer rotor 45, but the compressed air pressure causes the vane 42 to rotate.
  • the inclined protrusion 44 is pushed so as to be in contact with the inner surface of the outer rotor 45, and the circular portion 42 rotates a little more in the circular space 40 of the inner rotor 37, so that stable operation is possible. The airtightness is maintained.
  • FIGS. 4A to 4D show an operation state according to another embodiment of the present invention.
  • the air flowing in from the outside is the same as the vane 33 having the circular portion 62 inserted into the circular space 62 of the internal rotor 61 and the outside.
  • the protruding portion 65 where the inner rotor 61 and the outer rotor 67 are in contact with each other, the vane 63 and the working groove 66 are compressed in the compression chamber A whose volume is changed.
  • the outer rotor 67 rotated more than the inner rotor 61 in a state where the protruding portion 65 of the vane 63 in a state where the circular portion 64 was inserted into the circular hollow 62 of the inner rotor 61 was in contact with the operating groove 68.
  • the protrusion 65 of the vane 63 forms the curved surface 66 in the working groove 68 of the external rotor 67.
  • the state of the surface contact is maintained continuously, and at this time, the airtightness of the compression chamber A is maintained by the Apex seal (Seal) 69 of the circular hollow 62.
  • the pressure of the air compressed by the vane 63 is received in the direction of the arrow, but is offset by the pressure applied between the curved surface 66 of the projection 64 and the operating groove 68, so that a strong pressure is applied to the vane 63. I can't.
  • the inner rotor 61 and the outer rotor 67 rotate by about 180 °. Then, the volumes of the compression chamber A and the supply chamber B become almost equal, and the air in the compression chamber A is further compressed.
  • the vane 63 in which the circular portion 64 is inserted into the circular space 62 of the internal rotor 61 is located at the center of the working groove 68 of the external rotor 67.
  • the vane 63 in which the circular portion 64 is inserted into the circular hollow 62 of the internal rotor 61 is rotated slightly less than the external rotor 67, but due to the compressed air pressure.
  • the protruding part 65 of the vane 63 is pushed so as to be in contact with the insertion groove 68 of the external rotor 67, and the circular part 63 is slightly rotated in the circular hollow 62 of the internal rotor 61, so that stable operation is possible.
  • the airtightness of the compression chamber A is continuously maintained by the Apex seal (Seal) 69.
  • FIG. 5 is a longitudinal sectional view according to another embodiment of the present invention
  • FIG. 6 is a view schematically showing an operation process.
  • a fixed groove 73 is formed in a space 72 of the central bearing 71 which receives the rotational force from the outside through a motor (not shown),
  • a ring-shaped clamp 81 having one side opened is inserted into the circular cavity 80 of the internal rotor 77 so that the hermeticity is maintained by an Apex seal (Seal) 82.
  • the vane 87 of the outer rotor 86 is held in contact with the face 85 of the shoe 83 in which one end of the clamp 81 comes into surface contact with the curved groove 84.
  • the vane 87 of the outer rotor 86 is sandwiched between the clamps 81, and rotates together with the inner rotor 77.
  • the air supplied to the compression chamber A through the air supply air 89 of the bearing cover 88 is compressed by the state in which the volumes of the compression chamber A and the supply chamber B are changed by the
  • a compressed air storage chamber 91 is formed between the outer surface of the outer rotor 86 and the housing 90 to maintain a pressure equal to or higher than a predetermined pressure discharged through a discharge air 92 provided with a check valve 93 for preventing backflow of the outer rotor 86. After the compressed air is temporarily stored, it is discharged to an external tank.
  • the other fixed rod 76 is interposed between the fixing groove 79 of the space 78 and the internal rotor 77 is eccentric with the bearing 71. Compression is performed.
  • the ring-shaped clamp 81 inserted into the circular air space 80 of the internal rotor 77 flowing through the air supply air space 90 of the bearing cover 89 is attached to the Apex seal 82. Therefore, the inner rotor can be rotated while airtightness is maintained, and the vane 87 of the outer port 86 is in contact with the face 85 of the shell 83 where the curved groove 84 is in contact with the clamp 81. After being supplied to the supply chamber B defined by the outer rotor 86 and the van 87, it is compressed in the compression chamber A whose volume is changed by the inner rotor 77, the outer rotor 86 and the van 87. To do.
  • the air enters the supply chamber B, and the ring inserted into the circular hollow 80 of the internal rotor 77 receives the rotational force through the constant-force coupling 74 by the rotation of the bearing 71.
  • the clamp 81 having a shape is stably contacted by the shoe 83 while rotating, so that the vane 87 rotates rightward together with the inserted external rotor 86.
  • the ring-shaped clamp 81 inserted into the circular cavity 80 of the inner rotor 77 by the bearing 71 rotates together with the face 85 of the shoe 83 where the curved groove 84 contacts one end while rotating together.
  • the compression chamber A which was the supply chamber B, is sealed by the outer rotor 86, the vane 87, and the inner rotor 77.
  • the supply volume B is newly secured and air from outside flows in.
  • the airtightness of the clamp 81 inserted in the circular hollow 80 of the internal rotor 77 is maintained by the Apex seal (Seal) 82, and the external rotor 86 is held in a state where the vane 87 is sandwiched by the clamp 81. Is slightly more rotated than the inner rotor 77, but the clamp 81 into which the vane 87 is inserted rotates a little more in the circular hollow 80 of the inner rotor 77, so that the vane 87 of the outer rotor 86 is rotated.
  • the airtightness of the compression chamber is maintained while the one end of the clamp 81 and the vane 87 are in surface contact with the curved groove 84 and the face 85 of the shroud 83.
  • the airtightness of the clamp 81 inserted in the circular hollow 80 of the internal rotor 77 is maintained by the Apex seal (Seal) 82, and the external rotor 86 is held in a state where the vane 87 is sandwiched by the clamp 81.
  • the inner rotor 77 and the inner rotor 77 rotate in the same manner, so that the state in which the vane 87 of the outer rotor 86 is sandwiched can be continuously maintained, and one end of the clamp 81 is formed by the curved groove 84 and the face 85 of the shoe 83.
  • the airtightness of the compression chamber A is maintained while maintaining the state in which the vanes 87 are in surface contact.
  • the airtightness of the clamp 81 inserted in the circular hollow 80 of the internal rotor 77 is maintained by the Apex seal (Seal) 82, and the external rotor 86 is held in a state where the vane 87 is sandwiched by the clamp 81. Is rotated slightly less than the inner rotor 77, but the clamp 81 with the vane 87 inserted rotates slightly more in the circular space 80 of the inner rotor 77, so the vane 87 of the outer rotor 86 is pinched.
  • One end of the clamp 81 and the vane 87 can be maintained by the curved groove 84 and the face 85 of the shoe 83.
  • the airtightness of the compression chamber A is maintained while maintaining the surface contact state.
  • the airtightness is maintained while the face 85 of the shoe 83 sandwiched so that one end of the clamp 81 is in surface contact with the curved groove 84 while rotating together with the vane 87 of the external rotor 86.
  • the airtightness is maintained during rotation.
  • FIG. 7 is a diagram showing a configuration according to another embodiment of the present invention.
  • the circular hollow 93 of the inner rotor 92 has one side protruding portions 95, 97, and 99, and a ring-shaped clamp 94,%, 98.
  • the inner rotor 92 and the outer rotor 101 may be compressed in the compression chamber A whose volume is changed by the clamps 94, 96, 98 and the vane 101.
  • FIG. 8 is a longitudinal sectional view showing a structure according to another embodiment of the present invention
  • FIG. 9 is a transverse sectional view showing the structure of an internal rotor and an external rotor.
  • a space 114 is formed on one side of an inner rotor 111 having an air supply passage 113 provided in a central shaft 112,
  • an operation deviation 121 in which an air circulation passage 122 and an operation air 123 are formed and an operation deviation 126 in which an operation air 127 is formed are provided.
  • a semilunar elastic bias 125 is provided in the concave grooves 124, 129 of the inner peripheral surfaces of the two operating biases 121, 126, and due to this elasticity, the operating biases 121, 126 and the inner peripheral surface of the space 114 are formed. Airtightness is maintained between the inner peripheral surfaces of the space 114 by two Apex seals 117 while maintaining airtightness between
  • a ring gear 118 is formed on the inner surface of the recessed position, and a gear 135 is formed on the inner surface of the inner rotor 111 at a position recessed also at the center of the outer rotor 131.
  • a ring gear 134 that is a body
  • Gears 137 and 138 formed on the outer surface of a spherical linear gear 136 are inserted and eccentric to the gears 119 and 135 of the ring gears 118 and 134 of the inner rotor 111 and the outer rotor 131 so as to mesh with each other.
  • the inner rotor 111 and the outer rotor 131 are rotated at a constant speed.
  • a bearing 144, 145, 146, 147 are provided outside the inner rotor 111 and the outer rotor 131, a bearing 144, 145, 146, 147 are provided and the upper housing 141 and the lower housing 142 are connected,
  • Compressed air is supplied to an external compression tank (not shown) through an air supply path 143 connected to the outside to a lower housing 142 in which a closed compressed air storage chamber C is formed between the external rotor 131 and the external rotor 131.
  • the outer rotor 131 which is hermetically connected to the inner rotor 111, is configured such that the upper outer rotor 131a and the lower outer rotor 131b are connected by a number of bolts 139,
  • An upper housing 141 and a lower housing 142 which are hermetically connected to the outer rotor 131 may be connected by bolts 147 and nuts 148.
  • a ring gear is formed in a space portion of a central bearing portion that receives an external rotational force, and a line gear on one side is meshed with the ring gear.
  • a ring gear formed in a space portion of the internal rotor meshes with a line gear on the other side of the constant velocity pulling so that the ring gear rotates at a constant speed.
  • the other side of the vane compresses air in a state where the volumes of the compression chamber and the supply chamber are changed while being in contact with the operating groove of the external rotor. Therefore, high-pressure compressed air can be obtained in a small volume without generating noise due to collision.
  • FIG. 1 is a diagram showing the overall configuration of a conventional vane pump.
  • FIG. 2 is a diagram showing an overall configuration according to one embodiment of the present invention.
  • FIG. 3a to 3d are schematic diagrams illustrating an operation process according to one embodiment of the present invention.
  • FIG. 4a-d are schematic diagrams illustrating an operation process according to one embodiment of the present invention.
  • FIG. 4A to 4D are schematic views showing an operation process according to another embodiment of the present invention. 0 [Fig. 5]
  • FIG. 5 is a longitudinal sectional view showing an overall configuration according to one embodiment of the present invention. [Fig. 6a-d]
  • FIG. 6A to 6D are schematic views showing an operation process according to another embodiment of the present invention. [Fig. 7]
  • FIG. 7 is a cross-sectional view showing a configuration according to another embodiment of the present invention.
  • FIG. 8 is a longitudinal sectional view showing an overall configuration according to another embodiment of the present invention. [Fig. 9]
  • FIG. 9 is a cross-sectional view showing a configuration of an internal rotor and an external rotor according to another embodiment of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

Cette invention se rapporte à une pompe à palettes comportant un arbre central conçu pour être mis en rotation par une force extérieure, une couronne de train planétaire formée dans la partie creuse ménagée dans l'arbre, un engrenage linéaire formé au niveau d'une extrémité d'un organe de couplage à vitesse constante et engrené avec la couronne de train planétaire, et une couronne de train planétaire formée dans la partie creuse d'un rotor interne et engrenée avec l'engrenage linéaire formé au niveau de l'autre extrémité de l'organe de couplage à vitesse constante. Cet agencement permet de mettre en rotation l'arbre et le moteur interne à une même vitesse, d'insérer une partie circulaire formée au niveau d'une extrémité de palette à l'intérieur d'un espace creux circulaire du rotor interne, d'amener l'autre extrémité de la palette en contact avec une surface interne d'un rotor externe, et de faire varier le volume d'une chambre de compression et celui d'une chambre d'alimentation, l'air étant ainsi comprimé, ce qui permet à cette pompe à palettes de faible volume de produire de l'air comprimé à haute pression sans provoquer la collision de pièces susceptible de générer du bruit.
PCT/KR1998/000213 1997-07-16 1998-07-15 Pompe a palettes WO1999004167A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU84640/98A AU8464098A (en) 1997-07-16 1998-07-15 Vane pump

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1019970033359A KR100231475B1 (ko) 1997-07-16 1997-07-16 베인펌프
KR1997/33359 1997-07-16
KR1019970045563A KR100254171B1 (ko) 1997-09-02 1997-09-02 베인 펌프
KR1997/45563 1997-09-02
KR1019970050116A KR19990027626A (ko) 1997-09-30 1997-09-30 베인 펌프
KR1997/50116 1997-09-30

Publications (1)

Publication Number Publication Date
WO1999004167A1 true WO1999004167A1 (fr) 1999-01-28

Family

ID=27349575

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR1998/000213 WO1999004167A1 (fr) 1997-07-16 1998-07-15 Pompe a palettes

Country Status (2)

Country Link
AU (1) AU8464098A (fr)
WO (1) WO1999004167A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1177383A1 (fr) * 1999-04-23 2002-02-06 Dong Il Hwang Compresseur de petite taille
CN102678555A (zh) * 2011-03-18 2012-09-19 乐金电子(天津)电器有限公司 旋转式压缩机
JP2019038527A (ja) * 2017-07-26 2019-03-14 カンパニョーロ・ソシエタ・ア・レスポンサビリタ・リミタータＣａｍｐａｇｎｏｌｏ Ｓｏｃｉｅｔａ Ａ Ｒｅｓｐｏｎｓａｂｉｌｉｔａ Ｌｉｍｉｔａｔａ 自転車のフロントディレイラ作動装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246277A (en) * 1936-10-16 1941-06-17 Davidson William Ward Rotary pump
DE835121C (de) * 1949-11-05 1952-03-27 Fritz Schultheis Drehkolbenmaschine
DE2650320A1 (de) * 1976-11-02 1978-05-03 Alois Theisen Drehkolbenpumpe
JPS56159506A (en) * 1980-04-16 1981-12-08 Skf Kugellagerfabriken Gmbh Rotary piston machine
JPS6226393A (ja) * 1985-07-26 1987-02-04 Haradakuni:Kk 回転翼型コンプレツサ
JPS63112626U (fr) * 1987-01-14 1988-07-20
JPH01106985A (ja) * 1987-10-21 1989-04-24 Nippon Denso Co Ltd 圧縮機
JPH02169882A (ja) * 1988-12-21 1990-06-29 Mitsuo Okamoto 摺動受座式ベーンポンプ・ベーンモータ

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246277A (en) * 1936-10-16 1941-06-17 Davidson William Ward Rotary pump
DE835121C (de) * 1949-11-05 1952-03-27 Fritz Schultheis Drehkolbenmaschine
DE2650320A1 (de) * 1976-11-02 1978-05-03 Alois Theisen Drehkolbenpumpe
JPS56159506A (en) * 1980-04-16 1981-12-08 Skf Kugellagerfabriken Gmbh Rotary piston machine
JPS6226393A (ja) * 1985-07-26 1987-02-04 Haradakuni:Kk 回転翼型コンプレツサ
JPS63112626U (fr) * 1987-01-14 1988-07-20
JPH01106985A (ja) * 1987-10-21 1989-04-24 Nippon Denso Co Ltd 圧縮機
JPH02169882A (ja) * 1988-12-21 1990-06-29 Mitsuo Okamoto 摺動受座式ベーンポンプ・ベーンモータ

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1177383A1 (fr) * 1999-04-23 2002-02-06 Dong Il Hwang Compresseur de petite taille
EP1177383A4 (fr) * 1999-04-23 2004-08-04 Technol Co Ltd Dovicom Compresseur de petite taille
CN102678555A (zh) * 2011-03-18 2012-09-19 乐金电子(天津)电器有限公司 旋转式压缩机
JP2019038527A (ja) * 2017-07-26 2019-03-14 カンパニョーロ・ソシエタ・ア・レスポンサビリタ・リミタータＣａｍｐａｇｎｏｌｏ Ｓｏｃｉｅｔａ Ａ Ｒｅｓｐｏｎｓａｂｉｌｉｔａ Ｌｉｍｉｔａｔａ 自転車のフロントディレイラ作動装置

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