WO2002038964A1 - Pompe de moteur - Google Patents

Pompe de moteur Download PDF

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Publication number
WO2002038964A1
WO2002038964A1 PCT/JP2001/009680 JP0109680W WO0238964A1 WO 2002038964 A1 WO2002038964 A1 WO 2002038964A1 JP 0109680 W JP0109680 W JP 0109680W WO 0238964 A1 WO0238964 A1 WO 0238964A1
Authority
WO
WIPO (PCT)
Prior art keywords
motor
impeller
pump
casing
fixed shaft
Prior art date
Application number
PCT/JP2001/009680
Other languages
English (en)
Japanese (ja)
Inventor
Yoshio Miyake
Eiji Tsutsui
Original Assignee
Ebara Corporation
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 Ebara Corporation filed Critical Ebara Corporation
Priority to AU2002211011A priority Critical patent/AU2002211011A1/en
Publication of WO2002038964A1 publication Critical patent/WO2002038964A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0633—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/064—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/086—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/27—Rotor cores with permanent magnets
    • H02K1/2706—Inner rotors
    • H02K1/272—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis
    • H02K1/274—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of two or more circumferentially positioned magnets
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • the present invention relates to a motor pump, and more particularly, to a motor pump suitable for use in an area with a very small amount of water and a small output, using a motor having a permanent magnet on a motor rotor (for example, a DC brushless motor).
  • a motor having a permanent magnet on a motor rotor for example, a DC brushless motor.
  • positive displacement pumps such as gear pumps and diaphragm pumps are used as pumps incorporated in various devices and used at flow rates of 1 liter or less per minute to several liters per minute. Many.
  • This flow rate range is a region where the value of the specific speed N s is extremely small in the case of a centrifugal pump (non-positive displacement pump).
  • the value of the specific speed N s is 67 (mV)
  • the impeller outer diameter is about 25 mm.
  • a gear pump requires two shafts and two sets of bearings to rotate two gears, and is more complicated and expensive than a centrifugal pump.
  • diaphragm pumps are designed to repeatedly deform a non-metallic flexible diaphragm to send liquid. It is necessary to replace the diaphragm after about an hour of operation. For this reason, when the pump is used by being incorporated into various small devices, there is a problem that maintenance cost is excessively applied.
  • centrifugal motor pump which is suitable for use in the area of very small water volume and small output, replacing the positive displacement motor pump.
  • the centrifugal pump when the centrifugal pump is designed to rotate at higher speed, the specific speed of the larger value can be secured. That is, if a centrifugal pump with a flow rate of 1 liter per minute and a head of 10 meters is designed at a rotation speed of 1,800,000 revolutions per minute, the value of the specific speed Ns is 101 (m The pump efficiency can be expected to be improved to 3 min, m, and min.However, in this case, the outer diameter of the impeller is about 17 mm, and the entire impeller is extremely small, so that the axial thrust load can be supported. It becomes difficult to secure the mounting dimensions of the bearings and the flow area of the impeller suction part.
  • the present invention has been made in view of the above, and is suitable for use in an area with a very small amount of water and a small output, has a relatively simple structure, and can be made compact. It is intended to provide a pump.
  • a motor rotor having a cylindrical shape, a motor rotor having a permanent magnet, being integrally formed with the impeller, and disposed inside the motor stator, and covering the impeller.
  • a pump casing fixed to the open end of the motor casing, wherein a dynamic pressure bearing is provided between a front surface of the impeller and a spiral groove provided on an inner surface of the pump casing facing the front surface of the impeller. It is characterized by comprising.
  • a dynamic pressure bearing (axia) is compactly attached to the end of the motor rotor. Bearing) can be provided, and the bearing structure is simplified.
  • dynamic pressure bearings which are a type of non-contact type bearings, can be expected to have extremely high durability and can also function as a liner, thus reducing the number of parts. Therefore, the design that enables high-speed rotation makes it possible to achieve longer pump life and higher productivity while reducing the size and efficiency of the pump.
  • most of the axial load is absorbed by the permanent magnet of the motor rotor and the magnetic attraction of the motor stator.However, a dynamic pressure bearing is used to reinforce the absorption of the axial load.
  • the spiral groove is provided on a bearing plate fixed to a pump casing.
  • a motor stator having a cylindrical shape
  • a motor rotor having a permanent magnet, formed integrally with the impeller, and disposed inside the motor stator, and covering the impeller.
  • a pump casing fixed to the open end of the motor casing, the center hole provided in the shaft center of the motor rotor, and the pump casing protruding from the inner surface on the side opposite to the open end of the motor casing. It is characterized in that a radial bearing is formed between the fixed shaft and the fixed shaft.
  • the center hole communicates with a communication hole extending from a suction part of the impeller.
  • the handling liquid is applied, for example, to the ceramics on both the fixed side and the rotating side. It can be used for lubrication and cooling of the sliding part of the radial bearing part which is formed by applying a magnetic or Teflon resin coating, etc., and can surely lubricate and cool the sliding part.
  • the structure in which the center hole communicates with the communication hole extending from the suction portion of the impeller can also be used as a so-called balance piston that reduces the axial load (axial thrust load) generated on the motor rotor.
  • a motor rotor having a cylindrical shape, a permanent magnet, a motor rotor formed integrally with the impeller and disposed inside the motor stator, and covering the impeller.
  • a pump casing fixed to the open end of the motor casing, extending along the axis of the motor stator, and extending between the motor casing and the pump casing.
  • the suction port of the pump casing is provided at a position eccentric to the axis of the pump casing.
  • the axis of the suction port is located closer to the ground than the axis of the fixed shaft. It is configured as follows. BRIEF DESCRIPTION OF THE FIGURES
  • FIG. 1 is a sectional view of a motor pump according to a first embodiment of the present invention.
  • FIG. 2 is a surface view of a bearing plate constituting the dynamic pressure bearing on a side facing the front of the impeller.
  • FIG. 3 is a sectional view of a motor pump according to a second embodiment of the present invention.
  • FIG. 4 is a sectional view of a motor pump according to a third embodiment of the present invention.
  • a motor pump shown in c Figures 1 and 2 show a motor pump of the first embodiment of the present invention, have a cylindrical motor stator 1 0, the motor stator 1 Numeral 0 is integrally embedded in a cup-shaped motor casing 12 having one end closed and the other end opened, for example, by molding a polyester resin.
  • a fixed shaft 14 protruding inward along the axial direction is integrally connected to the motor casing 12 on the inner surface of the motor casing 12 on the side opposite to the opening.
  • the resin mold of the motor stator 10 is, for example, first applied to the inner periphery of the motor stator 10 in a state where the outer peripheral portion of a silicon steel plate or the like is positioned in a mold, and then molded. It is applied to the outer periphery of the motor stator 10 with the inner periphery of the motor stator 10 positioned in the mold.
  • the outer periphery of the motor stator 10 is not molded and painted. May be.
  • a substantially cylindrical motor rotor 20 is disposed inside the motor casing 12, and is disposed inside the motor rotor 20 along the axial direction from the side opposite to the opening of the motor casing 12.
  • a center hole 22 is provided which extends to near the center of the motor rotor 20.
  • a radial bearing portion 24 is formed between the inner peripheral surface of the center hole 22 and the outer peripheral surface of the fixed shaft 14. I have.
  • the inner diameter of the center hole 22 is set to, for example, about 6 mm, and the outer diameter of the fixed shaft 14 is set to be slightly smaller than the inner diameter of the center hole 22, respectively.
  • the ceramics A coating layer 26 is formed by a resin or Teflon resin coating, and a coating layer 28 is formed on the inner peripheral surface of the center hole 22 by a ceramic or Teflon resin coating. , 28 ensure the durability of the fixed shaft 14 and the center hole 22.
  • a tube made of Teflon having excellent slidability may be used.
  • the motor rotor 20 is made of, for example, a polyester resin. Inside the motor rotor 20, a ring-shaped permanent magnet 30 that rotates with the magnetic field generated by the motor stator 10 is provided at a position facing the motor stator 10. It is buried in one.
  • a closed impeller 32 having a front shroud is integrally connected to the motor rotor 20. Further, a small communication hole 34 having a diameter of, for example, about 1.5 mm is provided in the motor rotor 20 to communicate the center hole 22 with the suction portion of the impeller 32.
  • the structure in which the center hole communicates with the communication hole extending from the suction portion of the impeller is a so-called balance piston that reduces the axial load (axial thrust load) generated in the motor rotor 20. Can also be used.
  • a pump casing 44 having a suction nozzle 40 and a discharge nozzle 42, and having a shape of a pump which covers the periphery of the impeller 32. It is attached via a plurality of bolts and the like.
  • the pump casing 44 is made of, for example, a polyester resin, and an O-ring 46 is interposed between a contact portion between the motor casing 12 and the pump casing 44.
  • a bearing plate 50 made of, for example, stainless steel or Teflon resin is disposed at a position facing the front surface of the impeller 32 at the bottom of the pump casing 44 having a force-up shape.
  • a plurality of spiral grooves (spiral groups) 52 having a depth of about 0.01 mm are provided on the surface of the impeller 32 facing the front surface.
  • the bearing plate 50 is attached to the pump casing 44.
  • the pump casing and the bearing plate may be integrally formed of the same material.
  • a compact dynamic bearing (axial bearing) 54 can be provided at the end of the motor rotor 20 and the bearing structure is simplified.
  • the dynamic pressure bearing 54 a type of non-contact bearing, can be expected to have extremely high durability and can also function as a liner, thus reducing the number of parts. Therefore, the pump is designed to be able to rotate at high speeds, while miniaturizing the pump and increasing its efficiency, while extending the service life of the entire pump and improving productivity. Can also be achieved.
  • a dynamic bearing 54 is provided.
  • the motor in this motor pump is a DC brushless motor, and a current is supplied to the motor stator 10 from a power supply lead wire 56, and the motor is driven at a rotation speed of, for example, about 1800 rotations per minute. used.
  • motor pump of this embodiment when current is supplied to motor stator 10 from power supply lead wire 56, motor rotor 20 rotates, and suction from suction nozzle 40 of pump casing 44 is performed.
  • the collected liquid is pressurized by an impeller 32 that rotates integrally with the motor rotor 20, and most of the pressure is discharged from the discharge nozzle 42 to the outside of the pump casing 44.
  • a part of the treated liquid passes through the gap between the outer peripheral surface of the motor rotor 20 and the inner peripheral surface of the motor casing 12 after exiting from the impeller 32, and is guided to the radial bearing portion 24, where The sliding surface of the bearing portion 24 is lubricated and cooled, and then returns to the suction portion of the impeller 32 through the communication hole 34 of the shaft portion of the motor rotor 20.
  • the impeller 32 acting on the motor rotor 20 in the direction of The axial thrust load (axial load) is reduced.
  • a part of the liquid handled flows out of the impeller 32 and is guided to the dynamic pressure bearing 54, and after performing the bearing action as described above, returns to the suction portion of the impeller 32.
  • FIG. 3 is a diagram illustrating a motor pump according to a second embodiment of the present invention.
  • a ceramic rod member 60 is embedded in the inner surface of the motor casing 12 on the side opposite to the opening side so as to extend in the axial direction.
  • the rod member 60 protrudes inward along the axis, and the rod member 60 constitutes a fixed shaft 14.
  • Other configurations are the same as those of the first embodiment.
  • the fixed shaft 14 is made of a ceramic or the like, sufficient strength can be provided as the fixed shaft.
  • FIG. 4 is a diagram showing a motor pump according to a third embodiment of the present invention.
  • a fixed shaft made of ceramic and having a detent portion 62a, for example, having a diameter of about 3 mm, is provided between the motor casing 12 and the pump casing 44. 6, and the fixed shaft 62 is passed through a through-hole 64 extending along the axis of the motor rotor 20 to form a radial bearing portion 66.
  • the suction nozzle 40 of the pump casing 44 is located at a position eccentric to the axis 2 by a distance L.
  • a coating layer 68 is formed by ceramic or Teflon resin coating to ensure durability.
  • Other configurations are the same as those of the first embodiment.
  • suction nozzle 40 of the pump casing 44 is provided on the axis of the fixed shaft 62, it will be difficult to secure the suction passage area, and if the suction passage area is forcibly secured, Undesirable air pockets are created. However, according to this embodiment, such an adverse effect is caused by positioning the suction nozzle 40 of the pump casing 44 at a position eccentric from the axis of the fixed shaft 62 by the distance L. Can be prevented.
  • the shaft center of the suction nozzle 40 provided in the pump casing 44 is closer to the ground than the shaft center of the fixed shaft 62. Be level with the ground at the location. This reduces the flow passage area of the suction portion of the impeller 32 due to the presence of the fixed shaft 62. The amount of air trapped in the suction flow path can be substantially suppressed, and the handled liquid sucked from the suction nozzle 40 is released from the side periphery of the fixed shaft 62 and the impeller 3 It is led to the suction part of 2.
  • the present invention can be used for a motor pump used in a low output area with a very small amount of water, such as a flow rate range of 1 liter or less per minute to several liters.

Abstract

L'invention concerne une pompe de moteur centrifuge (déplacement non positif) utilisée dans une petite zone de sortie avec un volume d'eau extrêmement petit, de structure plutôt simple, et de petite taille. Ladite pompe de moteur comprend un stator tubulaire (10), un rotor (20) doté d'un aimant permanent (30) formé d'une seule pièce avec une roue à ailettes (32) disposée dans ledit stator (10), et un carter de pompe (44) fixé à un carter de moteur (12) de façon à recouvrir ladite roue à ailettes (32), un palier (54) de pression dynamique étant formé entre la face avant de la roue à ailettes (32) et une rainure spiralée (52) située sur la surface intérieure du carter de pompe (44) opposée à ladite face avant de la roue à ailettes (32).
PCT/JP2001/009680 2000-11-07 2001-11-06 Pompe de moteur WO2002038964A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002211011A AU2002211011A1 (en) 2000-11-07 2001-11-06 Motor pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000339170A JP2002138990A (ja) 2000-11-07 2000-11-07 モータポンプ
JP2000-339170 2000-11-07

Publications (1)

Publication Number Publication Date
WO2002038964A1 true WO2002038964A1 (fr) 2002-05-16

Family

ID=18814277

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/009680 WO2002038964A1 (fr) 2000-11-07 2001-11-06 Pompe de moteur

Country Status (3)

Country Link
JP (1) JP2002138990A (fr)
AU (1) AU2002211011A1 (fr)
WO (1) WO2002038964A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352487A1 (de) * 2003-07-22 2005-02-10 BSH Bosch und Siemens Hausgeräte GmbH Pumpe mit integriertem Motor
WO2007023014A1 (fr) * 2005-08-22 2007-03-01 Robert Bosch Gmbh Pompe centrifuge
WO2016016626A3 (fr) * 2014-07-28 2016-07-28 Cummins Ltd Turbo-générateur
CN106194763A (zh) * 2016-09-20 2016-12-07 浙江工业大学 高抗汽蚀的自吸离心泵
WO2018153605A1 (fr) * 2017-02-24 2018-08-30 Robert Bosch Gmbh Pompe à engrenage pour un système de récupération de chaleur
FR3065496A1 (fr) * 2017-04-25 2018-10-26 Saint Jean Industries Motopompe a rotor noye
CN110735794A (zh) * 2018-07-19 2020-01-31 安捷伦科技有限公司 具有油润滑真空泵的真空泵系统
JP2021173262A (ja) * 2020-04-30 2021-11-01 ダイハツ工業株式会社 電動ポンプ

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JP2004190562A (ja) * 2002-12-11 2004-07-08 Matsushita Electric Ind Co Ltd 小型渦流ポンプ
JP2007211691A (ja) * 2006-02-09 2007-08-23 Toyota Motor Corp ウォータポンプ
JP5326745B2 (ja) * 2009-03-31 2013-10-30 株式会社Ｉｈｉ タービン発電機
KR101307956B1 (ko) 2012-01-04 2013-09-12 캄텍주식회사 차량용 워터펌프
KR101250969B1 (ko) 2012-02-20 2013-04-05 캄텍주식회사 차량용 워터펌프
DE102013208476A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung
JP2015220910A (ja) * 2014-05-20 2015-12-07 株式会社不二工機 マグネットロータ式モータ及び当該モータを含むポンプ
JP6373059B2 (ja) * 2014-05-21 2018-08-15 株式会社不二工機 マグネットロータ式モータ及び当該モータを含むポンプ
EP3006742B1 (fr) * 2014-10-08 2021-12-01 Pierburg Pump Technology GmbH Pompe électrique à liquide de refroidissement pour véhicule automobile
CN106438501B (zh) * 2016-10-28 2019-11-22 浙江远邦流体科技有限公司 一体式转子轴向力自平衡离心泵、控制方法及终端
WO2019044737A1 (fr) * 2017-08-29 2019-03-07 テルモ株式会社 Dispositif de pompe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59165594U (ja) * 1983-04-20 1984-11-06 株式会社荏原製作所 シ−ルレスポンプ
JPS62148795U (fr) * 1986-03-12 1987-09-19
JPS6435098A (en) * 1987-07-30 1989-02-06 Ebara Corp Non-volumetric type pump
JPH01249996A (ja) * 1988-03-31 1989-10-05 Ebara Corp 高温気体用ブロワ
JPH02136594A (ja) * 1988-11-15 1990-05-25 Ebara Corp ポンプ装置
JPH10311293A (ja) * 1997-05-13 1998-11-24 Japan Servo Co Ltd キャンドモータポンプ

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59165594U (ja) * 1983-04-20 1984-11-06 株式会社荏原製作所 シ−ルレスポンプ
JPS62148795U (fr) * 1986-03-12 1987-09-19
JPS6435098A (en) * 1987-07-30 1989-02-06 Ebara Corp Non-volumetric type pump
JPH01249996A (ja) * 1988-03-31 1989-10-05 Ebara Corp 高温気体用ブロワ
JPH02136594A (ja) * 1988-11-15 1990-05-25 Ebara Corp ポンプ装置
JPH10311293A (ja) * 1997-05-13 1998-11-24 Japan Servo Co Ltd キャンドモータポンプ

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352487A1 (de) * 2003-07-22 2005-02-10 BSH Bosch und Siemens Hausgeräte GmbH Pumpe mit integriertem Motor
WO2007023014A1 (fr) * 2005-08-22 2007-03-01 Robert Bosch Gmbh Pompe centrifuge
WO2016016626A3 (fr) * 2014-07-28 2016-07-28 Cummins Ltd Turbo-générateur
US10605111B2 (en) 2014-07-28 2020-03-31 Cummins Ltd. Turbine generator with an internal rotor support shaft
CN106194763A (zh) * 2016-09-20 2016-12-07 浙江工业大学 高抗汽蚀的自吸离心泵
WO2018153605A1 (fr) * 2017-02-24 2018-08-30 Robert Bosch Gmbh Pompe à engrenage pour un système de récupération de chaleur
FR3065496A1 (fr) * 2017-04-25 2018-10-26 Saint Jean Industries Motopompe a rotor noye
WO2018197517A1 (fr) 2017-04-25 2018-11-01 Saint Jean Industries Motopompe a rotor noye
CN110735794A (zh) * 2018-07-19 2020-01-31 安捷伦科技有限公司 具有油润滑真空泵的真空泵系统
JP2021173262A (ja) * 2020-04-30 2021-11-01 ダイハツ工業株式会社 電動ポンプ

Also Published As

Publication number Publication date
AU2002211011A1 (en) 2002-05-21
JP2002138990A (ja) 2002-05-17

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