WO2007051360A1 - Pompe coulissante de facon radiale - Google Patents

Pompe coulissante de facon radiale Download PDF

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Publication number
WO2007051360A1
WO2007051360A1 PCT/CN2005/002108 CN2005002108W WO2007051360A1 WO 2007051360 A1 WO2007051360 A1 WO 2007051360A1 CN 2005002108 W CN2005002108 W CN 2005002108W WO 2007051360 A1 WO2007051360 A1 WO 2007051360A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
sliding
slider
fluid
radial
Prior art date
Application number
PCT/CN2005/002108
Other languages
English (en)
Chinese (zh)
Inventor
Gene Huang Yang
Original Assignee
Gene Huang Yang
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 Gene Huang Yang filed Critical Gene Huang Yang
Publication of WO2007051360A1 publication Critical patent/WO2007051360A1/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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F01C21/0827—Vane tracking; control therefor by mechanical means

Definitions

  • the invention relates to a fluid transfer device, and more particularly to a radial sliding push pump which draws a radial path through a rotor axis by means of an eccentric traction member for pulling a slider that rotates with the rotor
  • the reciprocating sliding further forms a suction and push action on the fluid in the flow passage, thereby pumping the fluid and changing the direction of rotation of the rotor to change the direction of the fluid transport path, thereby improving the usability.
  • the inventor of the present invention previously invented a fluid pump structure, which was approved by the Taiwanese Patent No. 137178 and the US 6,000, 921 invention patent, as shown in Figures 1 and 2, the conventional fluid pumps are mainly
  • the base 1 has an outer ring 2, a rotating disc 3 and a cover 4, wherein a side wall 101 is axially protruded from one side of the base 1 and the base 1 is parallel to the side.
  • a sliding groove 102 is disposed, and the outer ring 2 is interposed between the base 1 and the cover body 4, thereby forming an annular flow path 5 between the inner edge of the outer ring 2 and the ring wall 101.
  • the outer ring 2 corresponds to the two sliding slots 201 , and the sliding block 6 is clamped between the base 1 and the outer ring 2 , and the sliding strip 6 is disposed on the sliding slot 102 .
  • a first over-blocking groove 603 and a second over-blocking groove 604 are disposed, and the flow-path 5 is pivotally connected to each other adjacent to the sliding strip 6
  • the rotating disk 3 is pivoted against the end surface of the ring wall 101 to shield the flow path 5 from leaking.
  • the rotating disk 3 axially protrudes from a driving shaft 301.
  • the driving shaft 301 is coupled with the power source through the cover 4.
  • the rotating disk 3 is protruded from the rotating block 3 and is embedded in the flow channel 5, and the pushing block 302 is rotated in the flow channel 5 to push and transmit
  • the rotator 3 is eccentrically connected with a turret 303 embedded in the column space 602 for squeezing the slider 6 to linearly reciprocate.
  • the power source such as a motor or an engine drives the rotary disk 3 to rotate, and the eccentric shaft 303 that is eccentrically rotates along a circular path to pulsate the slide bar 6 to reciprocate.
  • the push block 302 is rotated in the flow path 5 so as to cooperate with the first and second check valves 501, 502
  • the fluid enters and exits the restriction of the flow path 5, and the fluid can be pumped.
  • the conventional fluid pump must use the first and second check valves 501, 502 to guide the direction of restricting the fluid into and out of the flow path 5, so as to achieve the purpose of effectively pumping the fluid, and the composition thereof is complicated, and only The fluid can be pumped from the source end to the destination end in a unidirectional manner, and the direction of the pumping cannot be selected, and the practical application forms a limit; if the fluid transfer direction needs to be changed, the first and second check valves 501 are required. 502, the external inlet pipe and the outlet pipe are respectively re-matched, or the first and second ⁇ return valves 501 and 502 are mutually arranged at the position of the base 1, and the piping or the check valve is disposed.
  • the conventional fluid pump occludes the annular flow path 5 by the reciprocal sliding of the sliding bar 6, so that when the push block 302 is rotated, the fluid can be sucked into the flow path at the rear end of the push block 302. a section, and pushing out the fluid in the flow path section of the front end of the push block 302. Therefore, in order to cooperate with the space required for the elongated slide bar 6, the base 1 is bound to have a relatively radial size. It is not conducive to the lightweighting of fluid pumps and their application in small flow systems.
  • a primary object of the present invention is to provide a radial sliding pump that pulls a slider that rotates with a rotor to reciprocate in a radial direction through a rotor axis by an eccentric traction member, thereby forming a pumping of fluid in the flow passage.
  • Suction and pushing action, according to pumping the transport fluid, and 'changing the direction of rotation of the rotor can change the direction of the path of fluid transfer, and then transfer the fluid in both directions, for the convenience of use.
  • a secondary object of the present invention is to provide a radial sliding push pump, wherein when the traction member is actuated, the traction member also reciprocates radially according to the slider, thereby sucking and pushing the fluid, and assisting the traction. Fluid pumping efficiency and smoothness of operation.
  • the present invention is a radial sliding push pump, which mainly comprises:
  • the pedestal is formed by a disk body forming a surrounding wall at a periphery thereof, and the pedestal is connected to the inner space of the surrounding wall through a guiding channel at both ends of the radial direction, and the rafting fluid passes through the guiding channel 3 ⁇ 4 the base, the inner wall of the surrounding wall respectively protrudes in a curved first and second flanges, and the flanges are respectively located between the guiding channels; a rotor is disposed in the inner space of the surrounding wall, and an outer circumference of the rotor is closely adhered to the curved inner edge of the flange, whereby a pair of flow passages are formed between the surrounding wall and the rotor, and the flow passages are symmetrically formed
  • the two sides of the flange are connected to the respective guide channels, and one end of the rotor is pivoted through the disk body to extend outside the base, and the driving device drives the rotor to rotate, and the other end of the rotor passes a sliding groove is defined in the
  • a slider is pivotally embedded in the sliding slot, and the axial length of the sliding block is shorter than the sliding slot, so that the sliding slot is formed at the outer end portion of the sliding block to communicate with the flow channel, and the sliding
  • the two ends of the block are in close contact with the first flange, and the slider portion is partially recessed into a groove;
  • a traction member is pivotally embedded in the recessed groove and abuts against the wall of the grooved groove.
  • the axis of the traction member is provided with a positioning rod, the axis of the positioning rod is parallel to the axis of the rotor, and the axis of the positioning rod is located at the axis
  • Each flange is connected to the center line of the rotor and deviated from the rotor axis, and the traction member is positioned to be offset from the axial center of the rotor, so that the slider is pulled by the traction member to reciprocally move along the axial direction of the sliding slot. Varying the transfer space by means of two-way pumping of the transport fluid; and
  • a cover is disposed on the edge of the surrounding wall to close the flow path, and the positioning rod is connected to the cover body for positioning the axis of the traction member.
  • Figure 1 is an exploded perspective view of the US 6, 000, 921 invention patent.
  • Figure 2 is a schematic diagram of the operation of the US 6, 000, 921 invention patent.
  • Figure 3 is a perspective view of a first embodiment of the present invention.
  • Figure 4 is a perspective exploded view of the first embodiment of the present invention.
  • Figure 5 is an axial cross-sectional view showing a first embodiment of the present invention.
  • Figure 6 is a sectional view taken along line 6-6 of Figure 5.
  • Fig. 7 is a first schematic view showing the state of operation of the first embodiment of the present invention.
  • Figure 8 is a second schematic view of the actuation state of the first embodiment of the present invention.
  • Figure 9 is a third schematic view of the actuation state of the first embodiment of the present invention.
  • Figure 10 is a fourth schematic view of the actuation state of the first embodiment of the present invention.
  • Figure 11 is a schematic view 5 showing the actuation state of the first embodiment of the present invention.
  • Figure 12 is a first schematic view of the reverse actuation state of the first embodiment of the present invention.
  • Figure 13 is a second schematic view of the reverse actuation state of the first embodiment of the present invention.
  • Figure 14 is a third schematic view of the reverse actuation state of the first embodiment of the present invention.
  • Figure 15 is an axial cross-sectional view showing a second embodiment of the present invention.
  • Figure 16 is a schematic longitudinal cross-sectional view showing a third embodiment of the present invention.
  • Figure 17 is an axial cross-sectional view showing a fourth embodiment of the present invention.
  • Figure 18 is an exploded perspective view showing a portion of a rotor, a slider and a tractor of a fifth embodiment of the present invention.
  • Figure 19 is an axial cross-sectional view showing a fifth embodiment of the present invention.
  • Figure 20 is a cross-sectional view taken along line 20-20 of Figure 19.
  • Figure 21 is a first schematic view of the actuation state of the fifth embodiment of the present invention.
  • Figure 22 is a second schematic view of the actuation state of the fifth embodiment of the present invention.
  • Figure 23 is a third schematic view of the actuated state of the fifth embodiment of the present invention.
  • Fig. 24 is a fourth schematic view showing the state of operation of the fifth embodiment of the present invention.
  • Figure 25 is an axial cross-sectional view showing a sixth embodiment of the present invention.
  • Figure 26 is an axial cross-sectional view showing a seventh embodiment of the present invention.
  • Base 110 disk body 111 surrounding wall 112
  • Base 310 surrounding wall 312 connecting pipe 3122
  • Traction piece 540 cover body 550 flow path 562
  • the first embodiment of the radial sliding push pump of the present invention mainly comprises a base 110, a rotor 120, a slider 130, a traction member 140 and a cover 150.
  • the pedestal 110 is formed by a disk body 111 having an annular surrounding wall 112 at a periphery thereof.
  • the surrounding wall 112 extends through a guiding channel 113, 114 and the surrounding wall 112 at opposite ends of the pedestal 110.
  • the inner space is connected to the inner wall of the surrounding wall 112, and the first and second flanges 115 and 116 are respectively convexly curved in the radial direction, and the flanges 115 and 116 are respectively located on the guiding passages 113 and 11 respectively.
  • the phase angle is exactly 90 degrees.
  • the susceptor 110 extends through a shaft hole 117 in the axial center of the disk body 111.
  • the rotor 120 is a circular block that is disposed in the inner space of the surrounding wall 112.
  • the outer circumference of the rotor 120 is closely adhered to the curved inner edge of the flanges 115 and 116, and the inner edge of the surrounding wall 112 is
  • a pair of arcuate flow paths 162, 164 are formed between the outer edges of the rotor 120, and the flow paths 162,
  • a symmetry is formed on the two sides of the flanges 115 and 116, and communicates with the guide channels 113 and 114 respectively.
  • the rotor 120 is axially disposed with a shaft 121 extending through the shaft hole 117 and extending from the base 110. Externally, the shaft 121 is rotated by a driving device such as a motor or an engine, and the rotor 120 is rotated inside the base 110, and the other end surface of the rotor 120 is radially recessed by a shaft thereof.
  • the groove 124 has a width that matches the width of the flanges 115 and 116, and the two ends of the sliding groove 124 respectively penetrate the outer circumference of the rotor 120.
  • the slider 130 is embedded in the elongated block of the sliding slot 124.
  • the axial length of the slider 130 is shorter than the sliding slot 124. Accordingly, the sliding slot 124 is disposed at the outer end of the slider 130.
  • the transfer space 163 is formed in the flow path 162, 164.
  • the end surface shape of the two ends of the slider 130 is matched with the inner edge surface of the first flange 115, and the slider 130 is reciprocally displaced inside the sliding groove 124. When moving, the two ends of the slider 130 are in close contact with the inner edge surface of the first flange 115.
  • the middle portion of the slider 130 is recessed into a recess 131, and the traction member 140 is embedded in the rectangular block of the recess 131.
  • the opposite side of the bearing member abuts against the slot wall of the slot 131.
  • the shaft of the traction member 140 is pivotally inserted into a positioning rod 142.
  • the end of the positioning rod 142 is coupled to the cover 150.
  • the positioning rod 142 is axially coupled to the shaft.
  • the axis of the rotor 120 and the cover 150 are parallel, and the axis of the positioning rod 142 is located at the center line of the flanges 115 and 116 and is offset from the axis of the rotor 120.
  • the traction member 140 is positioned to deviate from the rotor 120.
  • cover 150 is disposed at an edge of the surrounding wall 112 to close the flow path 162, 164.
  • a ring 171 is disposed between the 150 and the surrounding wall 112 to prevent fluid leakage.
  • a plurality of bolts 151 are protruded from the outer periphery of the cover body 150.
  • a plurality of other bolts 118 are protruded from the outer periphery of the base 110, and a plurality of bolts 172 are 172
  • the bolts 151 and the other bolt bases 118 are respectively threaded, and the bolts 172 are screwed to a nut 173 for coupling the base 110 and the cover body 150.
  • the pedestal 110 when the fluid is pumped by the first embodiment of the present invention, the pedestal 110 is connected to the conduits 113, 114, which are not connected to the respective conduits 113, 114.
  • the fluid enters and exits the base 110, and is driven by a motor or an engine to drive the rotor 120 through the shaft 121; when the slider 130 is in close contact with the first flange 115, 5 ⁇ 3 ⁇ 4
  • the transfer space 163 is formed between the other end of the slider 130 and the second flange 116, and the two sides of the transfer space 163 are the outer peripheral surface of the rotor 120 and the second flange 116.
  • the slot wall of the slot 131 forms a force couple effect on the traction member 140, so that the traction member 140 can rotate around the positioning rod 142, because The axial direction of the traction member 140 is offset from the axial center of the rotor 120 and is adjacent to the first flange 115.
  • the relative force of the traction member 140 on the slider 130 causes the slider 130 to direction the other end of the sliding slot 124.
  • the chute 124 is formed at the end of the slider 130 to form another transfer space 163' to communicate with the first-class channel 162.
  • the transfer spaces 163, 163' are respectively formed at two ends of the slider 130.
  • the transfer space 163 is in communication with the other flow path 164 due to the rotation of the rotor 120, and the other end of the slider 130 compresses the transfer space 163 to gradually reduce its volume as shown in FIG. 8, thus,
  • the other transfer space 163' is formed such that a negative pressure is formed inside the flow path 162, thereby causing the fluid to flow into the flow path 162 via an approach path 113, and the fluid inside the transfer space 163 and the other flow path 164 is Pressing of the slider 130
  • the squeezing flows out through the other approach channel 114; as shown in the ninth and tenth figures, when the rotation angle of the rotor 120 gradually approaches 180 degrees, the slider 130 is continuously displaced by the relative traction of the traction member 140, so that the other The transfer space 163' continues to expand, and the transfer space 163 continues to be reduced.
  • the flow path 162 is held in a negative pressure state to draw in fluid from the approach path 113 and accumulate in another transfer space 163', and the fluid in the transfer space 163 is subjected to the slider.
  • the continuous pushing of 130 is forced into another flow path 164 and flows out through another approach channel 114; when the rotor 120 is rotated by a 180 degree angle, the slider 130 is displaced to the other end of the chute 124, at this time, The transfer space 163 completely disappears due to the contact of the slider 130 with the first flange 115, and the other transfer space 163' accumulates fluid and opposes the second flange 116; thus by the rotor 120
  • the continuous rotation of the slider 130 is reciprocally displaced by the traction of the traction member 140, thereby forming a piston action on the space of the sliding groove 124 at both ends of the slider 130, so that the fluid can be sucked from the guide channel 113.
  • First class road 162 and transfer To the other flow path 164, it flows out through the
  • the fluid when the present invention is disposed in a flow path system as a device for pumping fluid, the fluid can be transferred bidirectionally by the change in the direction of rotation of the rotor 120, and there is no need to reconnect the piping of the flow path system or
  • the valve member can effectively improve the usability 5 and make the application scope wider, and has the industrial value of t3 ⁇ 4; on the other hand, the invention is compared with the US 6,000, 921 invention patent, fluid
  • the pumping space can be fully utilized, which is beneficial to lightweight and application in small flow systems, and In the implementation of the invention, only the axial distance between the traction member 140 and the rotor 120 is changed, and the size of the slider 130 is adjusted accordingly, so that the fluid pumping flow rate per unit time can be changed, which is beneficial to the base 110,
  • the mass production specifications of the rotor 120 and the tractor 140 are simplified.
  • the second embodiment of the present invention is slightly modified according to the foregoing first embodiment, and the same portions are not repeatedly described.
  • the second embodiment is mainly different in that the cover 250 is at the adjacent rotor 220.
  • a ring groove 252 is recessed, and a ring 225 is protruded from the end surface of the rotor 220.
  • the ring 225 is pivotally embedded in the ring groove 252.
  • the rotor 220 is The positioning of the rotor 220 can be prevented from being swayed during the rotation of the rotor 220, and the reliability of the rotor 220 can be improved.
  • annular groove 252 can be further embedded with an annular bushing 253 at the outer edge of the annular ring 225.
  • the ring 225 and the ring groove 252 are separated to avoid the relative wear of the ring 225 and the ring groove 252 to affect the positioning reliability of the rotor 220.
  • the third embodiment of the present invention is slightly modified according to the foregoing first embodiment.
  • the third embodiment is mainly different in that: the base 310 is respectively convex at the outer ends of the radial walls of the surrounding wall 312.
  • An adapter tube 3122, 3124 is provided, and the connection tubes 3122, 3124 are respectively connected to the flow channels 362, 364 through the respective approach channels 313, 314, and the base 310 can be connected to the fluid through the connection tubes 3122, 3124.
  • the base 310 is respectively convex at the outer ends of the radial walls of the surrounding wall 312.
  • An adapter tube 3122, 3124 is provided, and the connection tubes 3122, 3124 are respectively connected to the flow channels 362, 364 through the respective approach channels 313, 314, and the base 310 can be connected to the fluid through the connection tubes 3122, 3124.
  • the fourth embodiment of the present invention is slightly modified according to the foregoing first embodiment; referring to FIG. 17, the fourth embodiment is mainly different in that: the shaft 421 of the rotor 420 is further pivoted by a shaft seal 422 and a bearing. 423, to prevent the fluid from leaking at the abutment of the shaft 421 and the disk body 411 of the base 410 by the shaft seal 422, and reduce the friction between the shaft 421 and the disk body 411 according to the bearing 423, and improve the fluid. Pumping efficiency.
  • the fifth embodiment of the present invention is slightly modified according to the foregoing first embodiment; referring to FIG. 18 to FIG. 20, the fifth embodiment is mainly different in that: the rotor 520 is at the end surface of the adjacent cover 550, and the radial direction Two secondary flow passages 525 and 526 are formed.
  • the secondary flow passages 525 and 526 are respectively formed on both sides of the sliding groove 524 and perpendicular to the sliding groove 524, and the secondary flow passages 525 and 526 are end-mounted with the groove 531 of the slider 530.
  • the other ends of the auxiliary flow passages 525 and 526 are respectively connected to the respective flow passages 562 and 564.
  • the traction member 540 When the traction member 540 pulls the slider 530 to reciprocate, the traction member 540 is also radially opposed to the slider 530.
  • the slider 530 forms a reciprocating motion as shown in the twenty-first to the twenty-fourth embodiment; thus, the traction member 540 sucks the fluid in the first-pass channel 562 to enter the slot through a pair of flow passages 525.
  • the pumping efficiency when the two ends of the slider 530 are respectively opposed to the flanges 515, 516 of the base 510, can still be utilized by the formation of the secondary flow paths 525, 526.
  • the relative movement of the traction member 540 and the slider 530 continuously draws and pushes the fluid to provide a smoother pumping fluid.
  • the sixth embodiment of the present invention is slightly modified according to the foregoing first embodiment; referring to FIG. 25, the sixth embodiment is mainly different in that: the positioning rod 642 is connected to the shaft of the traction member 640 integrally, and At the other end, the pivot is inserted into the cover 650.
  • the seventh embodiment of the present invention is slightly modified according to the foregoing first embodiment; referring to FIG. 26, the seventh embodiment is mainly different in that: a bearing of the outer circumference of the rotor 720 and the disk 711 of the base 710 725, thereby reducing the relative friction between the rotor 720 and the disk 711, and improving the fluid pumping efficiency.
  • the present invention has undergone numerous trials to confirm that it can fully meet the intended purpose, and has excellent efficacy. It has not been seen in public publications and public use before application, and is in line with the requirements of invention patents, and submits applications according to law. The applicant will not be impressed if the trial is approved and the patent is granted as soon as possible.

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

Abstract

La présente invention concerne une pompe coulissante de façon radiale qui comprend essentiellement une base, un rotor, un coulisseau, une pièce de traction et un couvercle. Deux passages de fluide sont formés dans la base qui communique avec un passage de guidage. Le coulisseau est inséré de façon pivotante et radiale dans le rotor. La pièce de traction est montée de façon pivotante dans le coulisseau. L’axe de la pièce de traction est décalé par rapport à celui du rotor. Lorsque le coulisseau est entraîné en rotation par le rotor, le coulisseau tire sur la pièce de traction pour la faire tourner, la pièce de traction et le coulisseau ont un effet l’un sur l’autre afin de former une action de traction, alors le coulisseau se déplace en va-et-vient dans une direction radiale qui passe à travers l’axe du rotor. Le fluide est transféré parmi les passages de fluide, ce type de mécanisme peut pomper du fluide dans le sens des aiguilles d’une montre et dans le sens inverse des aiguilles d’une montre.
PCT/CN2005/002108 2005-11-01 2005-12-07 Pompe coulissante de facon radiale WO2007051360A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200510030923.2 2005-11-01
CNA2005100309232A CN1959114A (zh) 2005-11-01 2005-11-01 径向滑推式泵

Publications (1)

Publication Number Publication Date
WO2007051360A1 true WO2007051360A1 (fr) 2007-05-10

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Application Number Title Priority Date Filing Date
PCT/CN2005/002108 WO2007051360A1 (fr) 2005-11-01 2005-12-07 Pompe coulissante de facon radiale

Country Status (2)

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CN (1) CN1959114A (fr)
WO (1) WO2007051360A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011017817A1 (fr) * 2009-08-10 2011-02-17 Yang Genehuang Pompe d’oldham
CN105570130B (zh) * 2016-02-16 2018-11-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机泵体结构和压缩机
CN105570128B (zh) * 2016-02-16 2018-09-11 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机泵体结构及压缩机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707224A (en) * 1996-07-30 1998-01-13 Yang; Gene-Huang Liquid pump having an elongate slider and a pair of rotating disks
CN1198511A (zh) * 1997-05-07 1998-11-11 杨进煌 流体泵
US6000921A (en) * 1997-03-20 1999-12-14 Yang; Gene-Huang Fluid pump having a slider and a rotary disk

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707224A (en) * 1996-07-30 1998-01-13 Yang; Gene-Huang Liquid pump having an elongate slider and a pair of rotating disks
US6000921A (en) * 1997-03-20 1999-12-14 Yang; Gene-Huang Fluid pump having a slider and a rotary disk
CN1198511A (zh) * 1997-05-07 1998-11-11 杨进煌 流体泵

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