WO2013187786A1 - Electric pump motor cooled by closed circuit - Google Patents

Electric pump motor cooled by closed circuit Download PDF

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Publication number
WO2013187786A1
WO2013187786A1 PCT/PL2013/000077 PL2013000077W WO2013187786A1 WO 2013187786 A1 WO2013187786 A1 WO 2013187786A1 PL 2013000077 W PL2013000077 W PL 2013000077W WO 2013187786 A1 WO2013187786 A1 WO 2013187786A1
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WO
WIPO (PCT)
Prior art keywords
impeller
heat exchanger
heat
coolant
electric motor
Prior art date
Application number
PCT/PL2013/000077
Other languages
French (fr)
Inventor
Marcin JANCZAK
Wojciech Plutecki
Sebastian PREDEL
Original Assignee
Hydro - Vacuum Spółka Akcyjna
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 Hydro - Vacuum Spółka Akcyjna filed Critical Hydro - Vacuum Spółka Akcyjna
Publication of WO2013187786A1 publication Critical patent/WO2013187786A1/en

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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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • 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 invention discloses the electric motor for pumps with an internal cooling system for use in dry conditions, although exposed to medium, rain or flood water.
  • the motor may also be used in submersible pump designs.
  • Electric motors driving the pumps generate a large amount of heat, which may cause motor damage, if the heat is not dissipated.
  • the damage may require further motor repairs and/or replacement and may cause pump standstill. Even the short standstill may cause serious issues, i.e. flooding drained areas with water, sewage or other medium.
  • the motor for pumps intended for operation in dry conditions may be flooded with the medium.
  • submersible pump designs are used. The submersible pump design allows motor cooling as a result of natural convection, where the heat generated by the motor is dissipated through the housing to the medium. The disadvantage in this case is the need to maintain a specific medium level to ensure efficient pump cooling.
  • the medium may never be completely removed, and the remaining medium may decay and cause unpleasant smells.
  • This can be avoided by using the pumps with a body incorporating a jacket surrounding the motor, through which a coolant circulates.
  • the medium is forced into the jacket as a result of pump impeller rotation.
  • the medium dissipates heat generated by the motor as a result of forced convection.
  • the disadvantage is sedimentation of medium deposits inside the jacket. The deposits may cause clogging and reduce heat transfer resulting in motor overheating. Also high medium pressure may damage the body.
  • motors with an internal cooling system. In this case, the heat is received by a coolant in a closed loop system and is transferred to the medium through the wall separating the motor and the pump.
  • the coolant must circulate.
  • the circulation is obtained with an impeller installed inside the cooling system.
  • the impeller ensures circulation of coolant, which receives the heat and transfers the heat to the medium via a heat exchanger. Heat transfer efficiency depends on coolant flow rate along the heat exchanger with the medium around it.
  • the electric motor particularly for pumps with an internal cooling system is known from the German patent application DE 10317492.
  • the impeller forcing coolant circulation is installed over the motor, whereas the heat exchanger transferring the coolant heat to the medium is on the opposite side of the motor.
  • a centrifugal impeller with axial flow or diagonal impeller is required.
  • Use of those impellers to increase the flow rate along the heat-transferring wall requires relatively high energy. It thus reduces drive motor efficiency and increases operating costs.
  • the disadvantage is that even the insignificant assembly errors affect impeller performance. A gap between the impeller and the housing must be controlled, since even the small gap causes reduction in impeller performance and affects coolant flow rate.
  • the solution features an internal cooling system with an impeller induced flow.
  • the coolant's impeller is not driven directly by the motor shaft but via a system of gears.
  • the impeller axis is perpendicular to the motor shaft axis.
  • the solution is very complex and requires additional components, which not only increases the device costs but also maintenance and repair costs. Also, to ensure proper coolant flow rate, centrifugal or diagonal impeller is required in this solution.
  • the disadvantage is a high power demand, complex design, and high costs. Also use of the gears to drive the motor affects design and assembly complexity, as well as precision. All impeller assembly errors, axial displacement or impeller play reduce impeller performance.
  • the aim is to develop an electric motor, especially for impeller pumps with an internal cooling system, which will be the solution to the issues presented above, and will be characterized both by a high efficiency and a simple design.
  • the present invention discloses an electric motor for pumps with an internal cooling system comprising a cooling jacket further including two separated walls with a void between said walls filled with a coolant, receiving heat generated by the motor as a result of convection, whereas the cooling jacket is connected via an inlet channel and a surge chamber to a suction chamber, further including motor shaft driven impeller, downstream of the impeller, at the coolant outflow, is a heat exchanger with a wall in contact with the working chamber of the pump, transferring the heat generated by the motor to the coolant, whereas downstream of the heat exchanger is an outflow channel connected to the jacket,
  • an axial flow multi-blade impeller is mounted on the motor shaft, between the seal, where the impeller hub diameter dp to external impeller diameter do ratio is 0.3 to 0.99 and the number of blades is 2 to 50, whereas the kinematic specific speed is ⁇ 800.
  • the beginning of a heat-transferring wall, transferring heat to the coolant, as part of a heat exchanger, further including a heat exchanger channel and a heat exchanger chamber is in the distance equal to 0 to 10 times the external impeller diameter do.
  • Use of axial flow multi-blade impeller with specified parameters ensures high peripheral speed component of the heated coolant flow rate, which due to near location of the beginning of the heat-transferring wall quickly flows to the heat exchanger.
  • the height h of the heat exchanger channel and the heat exchanger chamber may be variable.
  • the heat-transferring wall at the heat exchanger chamber section is fitted with ribs positioned in accordance with the direction of medium outflow from the impeller.
  • the heat-transferring wall at the heat exchanger chamber section is cylinder shaped.
  • the heat-transferring wall at the heat exchanger chamber section is conical shaped.
  • the heat- transferring wall at the heat exchanger chamber section is ring shaped.
  • the impeller hub diameter dp to external diameter do ratio is 0.7 to 0.99.
  • the number of impeller blades is 8 to 50.
  • the kinematic specific speed is ⁇ 130.
  • the coolant is a water and glycol solution.
  • the coolant is oil.
  • the solution in the present invention provides fast and efficient cooling of the heated coolant.
  • the advantage of the solution of the present invention is high coolant flow rate along the wall, transferring the heat to the pumped medium without significant increase in system energy demand.
  • the other advantage of the axial flow impeller is simple design compared to centrifugal flow or diagonal impellers. The simple design reduces the effect of assembly errors on impeller performance, i.e. excessive gap size between the impeller and the housing. Also wear of system components of the present invention has an insignificant effect on system efficiency, compared to the prior art solutions.
  • fig. 1 shows the impeller pump view driven by an electric motor with an internal cooling system
  • fig. 2 shows the detail of a pump view with an axial impeller and a heat exchanger.
  • the electric motor for pumps with an internal cooling system comprises a cast iron body 1 further including a motor shaft 2, a motor impeller 3_ and a motor stator A jacket 5_ comprising two parallel walls _ and 7. i n a specific distance is fitted around the motor.
  • the distance between the walls 6 and 1_ is filled with a coolant, comprising 70% water and 30% glycol solution.
  • the coolant chemical constitution prevents freezing at low temperatures, if the motor is not working.
  • the heated coolant flows to a surge chamber 9_ via an inflow channel 8. From the surge chamber 9_, the heated coolant flows to a suction chamber 1_0 installed over the impeller 11, said impeller coaxially mounted on the motor shaft 2_.
  • the impeller 11_ is of axial flow multi-blade type.
  • the impeller hub diameter dp to external impeller diameter do ratio is 0.9.
  • the impeller 11 comprises fourteen slanting blades 12_.
  • the impeller 11 kinematic specific speed is 50.
  • Use of the axial flow impeller causes high peripheral speed component of the medium.
  • the increase in peripheral medium speed improves heat dissipation by the coolant.
  • the beginning of the heat- transferring wall 13_ is directly downstream of the impeller 11 at the coolant outflow.
  • the distance between the beginning of the heat-transferring wall 13_ and the impeller 11. is 0.05 times the impeller external diameter do.
  • the coolant flows through the heat exchanger channel 14 to the heat exchanger chamber 15 along the heat-transferring wall 13_.
  • the heat accumulated by the coolant penetrates the heat-transferring wall 13_ and is received by the medium pumped on the opposite side of the wall by the pump" impeller 18_.
  • the heat- transferring wall 13_ at the heat exchanger chamber 15 section is fitted with ribs _16 positioned in accordance with the direction of medium outflow from the impeller.
  • the heat- transferring wall 13_ at the heat exchanger channel 14_ section is conical shaped.
  • the shape allows easy change in the direction of medium outflow from the impeller from axial to centrifugal, without excessive energy losses, and the area of heat-transmitting wall 13_ in contact with the medium is increased. It ensures longer heat exchange period, resulting in improved exchange of heat accumulated by the coolant.
  • the heat exchanger channel 1_4 height h is twice as low as the heat exchanger chamber 1_5 height. The height h means, that the coolant flow rate will not change both in the heat exchanger channel and the chamber, despite additional ribs in the heat exchanger chamber, reducing heat exchanger cross section. It maintains high constant flow rate and improves heat convection with low energy losses. Following the heat transfer, the coolant flows via the outflow channel 1T_ back to the jacket 5, where it receives heat generated by the electric motor. To ensure cooling system integrity, two seals 19 and 2_0 are installed on both sides of the impeller 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses an electric motor for pumps with an internal cooling system. The closed loop cooling system comprises a cooling jacket (5) further including two separated walls (6) and (1) with a void between the walls filled with a coolant, transferring heat generated by the motor. The cooling jacket (5) is connected via an inlet channel (8) and a surge chamber (9) to a suction chamber (10), further including an axial flow multi-blade impeller (11). The impeller is fitted between two seals (19) and (20). The impeller (11) hub diameter dp to external diameter do ratio is 0.3 to 0.99 and the number of blades (12) is 2 to 50, whereas the kinematic specific speed is <800. The beginning of a heat-transferring wall (13), transferring heat to the coolant, as part of a heat exchanger, further including a heat exchanger channel (14) and a heat exchanger chamber (15) is in the distance equal to 0 to 10 times the external impeller (11) diameter do. A height h of the heat exchanger channel (14), receiving the heated coolant and the heat exchanger chamber (15) is equal to the result of the following operation: h= [0.25, 6 ] * (do-dp) ÷2, where [0.25, 6] is a closed set within the range of 0.25 to 6, do is the external impeller diameter, and dp is the impeller hub diameter.

Description

ELECTRIC PUMP MOTOR COOLED BY CLOSED CIRCUIT
The invention discloses the electric motor for pumps with an internal cooling system for use in dry conditions, although exposed to medium, rain or flood water. The motor may also be used in submersible pump designs.
Electric motors driving the pumps generate a large amount of heat, which may cause motor damage, if the heat is not dissipated. The damage may require further motor repairs and/or replacement and may cause pump standstill. Even the short standstill may cause serious issues, i.e. flooding drained areas with water, sewage or other medium. In certain cases, the motor for pumps intended for operation in dry conditions may be flooded with the medium. In case there is a risk of motor being flooded, submersible pump designs are used. The submersible pump design allows motor cooling as a result of natural convection, where the heat generated by the motor is dissipated through the housing to the medium. The disadvantage in this case is the need to maintain a specific medium level to ensure efficient pump cooling. It means that the medium may never be completely removed, and the remaining medium may decay and cause unpleasant smells. This can be avoided by using the pumps with a body incorporating a jacket surrounding the motor, through which a coolant circulates. The medium is forced into the jacket as a result of pump impeller rotation. The medium dissipates heat generated by the motor as a result of forced convection. The disadvantage is sedimentation of medium deposits inside the jacket. The deposits may cause clogging and reduce heat transfer resulting in motor overheating. Also high medium pressure may damage the body. Those issues can be addressed by using motors with an internal cooling system. In this case, the heat is received by a coolant in a closed loop system and is transferred to the medium through the wall separating the motor and the pump. To ensure efficient motor cooling as a result of convection, the coolant must circulate. The circulation is obtained with an impeller installed inside the cooling system. The impeller ensures circulation of coolant, which receives the heat and transfers the heat to the medium via a heat exchanger. Heat transfer efficiency depends on coolant flow rate along the heat exchanger with the medium around it.
The electric motor, particularly for pumps with an internal cooling system is known from the German patent application DE 10317492. In this solution, the impeller forcing coolant circulation is installed over the motor, whereas the heat exchanger transferring the coolant heat to the medium is on the opposite side of the motor. To ensure high coolant flow rate and optimum heat convection to the medium, a centrifugal impeller with axial flow or diagonal impeller is required. Use of those impellers to increase the flow rate along the heat-transferring wall requires relatively high energy. It thus reduces drive motor efficiency and increases operating costs. The disadvantage is that even the insignificant assembly errors affect impeller performance. A gap between the impeller and the housing must be controlled, since even the small gap causes reduction in impeller performance and affects coolant flow rate.
WILO have presented a solution in the US patent no.
2009324436 "FA submersible pump with FKT 27 motor". The solution features an internal cooling system with an impeller induced flow. In this case, as opposed to the above solution, the coolant's impeller is not driven directly by the motor shaft but via a system of gears. The impeller axis is perpendicular to the motor shaft axis. The solution is very complex and requires additional components, which not only increases the device costs but also maintenance and repair costs. Also, to ensure proper coolant flow rate, centrifugal or diagonal impeller is required in this solution. The disadvantage is a high power demand, complex design, and high costs. Also use of the gears to drive the motor affects design and assembly complexity, as well as precision. All impeller assembly errors, axial displacement or impeller play reduce impeller performance.
The aim is to develop an electric motor, especially for impeller pumps with an internal cooling system, which will be the solution to the issues presented above, and will be characterized both by a high efficiency and a simple design.
The present invention discloses an electric motor for pumps with an internal cooling system comprising a cooling jacket further including two separated walls with a void between said walls filled with a coolant, receiving heat generated by the motor as a result of convection, whereas the cooling jacket is connected via an inlet channel and a surge chamber to a suction chamber, further including motor shaft driven impeller, downstream of the impeller, at the coolant outflow, is a heat exchanger with a wall in contact with the working chamber of the pump, transferring the heat generated by the motor to the coolant, whereas downstream of the heat exchanger is an outflow channel connected to the jacket, According to the invention, an axial flow multi-blade impeller is mounted on the motor shaft, between the seal, where the impeller hub diameter dp to external impeller diameter do ratio is 0.3 to 0.99 and the number of blades is 2 to 50, whereas the kinematic specific speed is ≤800. The beginning of a heat-transferring wall, transferring heat to the coolant, as part of a heat exchanger, further including a heat exchanger channel and a heat exchanger chamber is in the distance equal to 0 to 10 times the external impeller diameter do. Use of axial flow multi-blade impeller with specified parameters ensures high peripheral speed component of the heated coolant flow rate, which due to near location of the beginning of the heat-transferring wall quickly flows to the heat exchanger. A height h of the heat exchanger channel , receiving the heated coolant and the heat exchanger chamber is equal to the result of the following operation: h= [0.25 , 6] * {do-dp) ÷2 , where [0.25 , 6] is a closed set within the range of 0.25 to 6, do is the external impeller diameter, and dp is the impeller hub diameter.
The height h of the heat exchanger channel and the heat exchanger chamber may be variable. The heat-transferring wall at the heat exchanger chamber section is fitted with ribs positioned in accordance with the direction of medium outflow from the impeller. Preferably, the heat-transferring wall at the heat exchanger chamber section is cylinder shaped. Preferably, the heat-transferring wall at the heat exchanger chamber section is conical shaped. Preferably, the heat- transferring wall at the heat exchanger chamber section is ring shaped. Preferably, the impeller hub diameter dp to external diameter do ratio is 0.7 to 0.99. Preferably, the number of impeller blades is 8 to 50. Preferably, the kinematic specific speed is ≤130. The coolant is a water and glycol solution. Preferably, the coolant is oil.
The solution in the present invention provides fast and efficient cooling of the heated coolant. The advantage of the solution of the present invention is high coolant flow rate along the wall, transferring the heat to the pumped medium without significant increase in system energy demand. The other advantage of the axial flow impeller is simple design compared to centrifugal flow or diagonal impellers. The simple design reduces the effect of assembly errors on impeller performance, i.e. excessive gap size between the impeller and the housing. Also wear of system components of the present invention has an insignificant effect on system efficiency, compared to the prior art solutions.
The embodiment of the present invention is showed in the following figures, where fig. 1 shows the impeller pump view driven by an electric motor with an internal cooling system, whereas fig. 2 shows the detail of a pump view with an axial impeller and a heat exchanger.
In the embodiment, the electric motor for pumps with an internal cooling system comprises a cast iron body 1 further including a motor shaft 2, a motor impeller 3_ and a motor stator A jacket 5_ comprising two parallel walls _ and 7. in a specific distance is fitted around the motor. The distance between the walls 6 and 1_ is filled with a coolant, comprising 70% water and 30% glycol solution. The coolant chemical constitution prevents freezing at low temperatures, if the motor is not working. The heated coolant flows to a surge chamber 9_ via an inflow channel 8. From the surge chamber 9_, the heated coolant flows to a suction chamber 1_0 installed over the impeller 11, said impeller coaxially mounted on the motor shaft 2_. The impeller 11_ is of axial flow multi-blade type. The impeller hub diameter dp to external impeller diameter do ratio is 0.9. The impeller 11 comprises fourteen slanting blades 12_. The impeller 11 kinematic specific speed is 50. Use of the axial flow impeller causes high peripheral speed component of the medium. The increase in peripheral medium speed improves heat dissipation by the coolant. The beginning of the heat- transferring wall 13_ is directly downstream of the impeller 11 at the coolant outflow. The distance between the beginning of the heat-transferring wall 13_ and the impeller 11. is 0.05 times the impeller external diameter do. Heated coolant flowing out of the impeller _11 at high speed flows to the beginning of the heat-transferring wall 13_, as part of the heat exchanger further including a heat exchanger channel 14 and a heat exchanger chamber 15_. The coolant flows through the heat exchanger channel 14 to the heat exchanger chamber 15 along the heat-transferring wall 13_. The heat accumulated by the coolant penetrates the heat-transferring wall 13_ and is received by the medium pumped on the opposite side of the wall by the pump" impeller 18_. To ensure better heat convection between the wall and the medium, the heat- transferring wall 13_ at the heat exchanger chamber 15 section is fitted with ribs _16 positioned in accordance with the direction of medium outflow from the impeller. Also the heat- transferring wall 13_ at the heat exchanger channel 14_ section is conical shaped. The shape allows easy change in the direction of medium outflow from the impeller from axial to centrifugal, without excessive energy losses, and the area of heat-transmitting wall 13_ in contact with the medium is increased. It ensures longer heat exchange period, resulting in improved exchange of heat accumulated by the coolant. The heat exchanger channel 1_4 height h is twice as low as the heat exchanger chamber 1_5 height. The height h means, that the coolant flow rate will not change both in the heat exchanger channel and the chamber, despite additional ribs in the heat exchanger chamber, reducing heat exchanger cross section. It maintains high constant flow rate and improves heat convection with low energy losses. Following the heat transfer, the coolant flows via the outflow channel 1T_ back to the jacket 5, where it receives heat generated by the electric motor. To ensure cooling system integrity, two seals 19 and 2_0 are installed on both sides of the impeller 11.

Claims

Claims
An electric motor for pumps with an internal cooling system, wherein the internal cooling system comprises a cooling jacket further including two separated walls with a void between the walls filled with a coolant, transferring heat generated by the motor, whereas the cooling jacket is connected via an inlet channel and a surge chamber to a suction chamber, further including motor shaft driven impeller, downstream of said impeller, at the coolant outflow, is a heat exchanger with a wall in contact with a working chamber of said pump, transferring heat generated by the motor from the coolant to the medium, downstream of said heat exchanger is an outlet channel connected to said jacket, wherein an axial flow multi-blade impeller (11) is installed on a motor shaft
(2) between two seals (19_) and (20) , wherein said impeller (11_) hub diameter dp to external impeller (11) diameter do ratio is 0.3 to 0.99 and the number of blades (12_) is 2 to 50, whereas the kinematic specific speed is <800, the beginning of said heat- transferring wall (13_) , as part of a heat exchanger, further including a heat exchanger channel and a heat exchanger chamber (15) is in the distance of 0 to 10 times the external impeller (1Λ) diameter do, the height h of said heat exchanger channel , receiving the heated coolant and said heat exchanger chamber (15 ) is equal to the result of the following operation: h= [0.25 , 6] * (do-dp) ÷2 , where [0.25 , 6] is a closed set within the range of 0.25 to 6, do is the external impeller diameter, and dp is the impeller hub diameter. An electric motor according to claim 1, wherein the height h of the heat exchanger channel (1_4) and the heat exchanger chamber (15) is variable.
3. An electric motor according to claim 1, wherein the heat-transmitting wall (13) at the heat exchanger chamber (15_) section comprises ribs (16) positioned in accordance with the coolant outflow direction.
4. An electric motor according to claim 1, wherein the heat-transmitting wall (13_) at the heat exchanger chamber (14) section is cylinder shaped.
5. An electric motor according to claim 1, wherein the heat- transmitting wall (13_) at the heat exchanger chamber (14) section is conical shaped.
6. An electric motor according to claim 1, wherein the heat-transmitting wall (13_) at the heat exchanger chamber (14) section is ring shaped.
7. An electric motor according to claim 1, wherein the impeller (11) hub diameter dp to external diameter do ratio is 0.7 to 0.99.
8. An electric motor according to claim 1, wherein the number of blades (12_) of the impeller (11_) is 8 to 50.
9. An electric motor according to claim 1, wherein the specific speed is ≤130.
10. An electric motor according to claim 1, wherein the coolant comprises water and glycol solution.
11. An electric motor according to claim 1, wherein the coolant comprises oil.
PCT/PL2013/000077 2012-06-14 2013-06-10 Electric pump motor cooled by closed circuit WO2013187786A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PLP-399512 2012-06-14
PL399512A PL224743B1 (en) 2012-06-14 2012-06-14 Electric motor for pumps with a closed liquid cooling system

Publications (1)

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WO2013187786A1 true WO2013187786A1 (en) 2013-12-19

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WO (1) WO2013187786A1 (en)

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DE102015012277A1 (en) 2015-09-24 2017-03-30 Ebm-Papst St. Georgen Gmbh & Co. Kg fan unit
CN107565756A (en) * 2016-06-30 2018-01-09 上海汽车集团股份有限公司 Oil pump electrical machinery, gearbox and automobile
WO2020111186A1 (en) * 2018-11-30 2020-06-04 株式会社鶴見製作所 Underwater pump
CN111295521A (en) * 2017-11-01 2020-06-16 株式会社Ihi Centrifugal compressor
WO2021013782A1 (en) * 2019-07-23 2021-01-28 KSB SE & Co. KGaA Pump assembly comprising a lubrication- and cooling system
EP3882468A1 (en) * 2020-03-17 2021-09-22 Garrett Transportation I Inc. Compressor with cooled air passage and liquid coolant passage in axial heat exchanger arrangement
DE202020104824U1 (en) 2020-08-20 2021-11-26 K.H. Brinkmann GmbH & Co Kommanditgesellschaft Medium-cooled liquid pump
US11339800B2 (en) 2017-11-01 2022-05-24 Ihi Corporation Centrifugal compressor with heat exchanger
US11913473B2 (en) 2020-03-17 2024-02-27 Garrett Transportation I Inc Compressor with electric motor coolant jacket having radial and axial portions

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DE10317492A1 (en) 2002-05-07 2003-11-20 Emu Unterwasserpumpen Gmbh Drive motor, especially for a pump
US20090324436A1 (en) 2006-08-26 2009-12-31 Wilo Ag Motor centrifugal pump having coolant pump

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Publication number Priority date Publication date Assignee Title
DE10208688A1 (en) * 2002-02-28 2003-09-18 Abs Pump Ct Gmbh Immersed motor pump has housing with motor and pump sections connected by intermediate chamber coupled with cooling jacket for motor
DE10317492A1 (en) 2002-05-07 2003-11-20 Emu Unterwasserpumpen Gmbh Drive motor, especially for a pump
US20090324436A1 (en) 2006-08-26 2009-12-31 Wilo Ag Motor centrifugal pump having coolant pump

Cited By (19)

* Cited by examiner, † Cited by third party
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CN105782064A (en) * 2015-01-14 2016-07-20 科普莱赛泰克公司 Electric pump
EP3045735A1 (en) * 2015-01-14 2016-07-20 Coprececitec, S.L. Electric pump
DE102015012277A1 (en) 2015-09-24 2017-03-30 Ebm-Papst St. Georgen Gmbh & Co. Kg fan unit
US11536278B2 (en) 2015-09-24 2022-12-27 Ebm-Papst St. Georgen Gmbh & Co. Kg Blower unit
CN107565756A (en) * 2016-06-30 2018-01-09 上海汽车集团股份有限公司 Oil pump electrical machinery, gearbox and automobile
CN107565756B (en) * 2016-06-30 2020-03-10 上海汽车集团股份有限公司 Oil pump motor, gearbox and car
CN111295521A (en) * 2017-11-01 2020-06-16 株式会社Ihi Centrifugal compressor
US11339800B2 (en) 2017-11-01 2022-05-24 Ihi Corporation Centrifugal compressor with heat exchanger
US11248612B2 (en) 2017-11-01 2022-02-15 Ihi Corporation Centrifugal compressor with gas and liquid cooling lines
JP7067443B2 (en) 2018-11-30 2022-05-16 株式会社鶴見製作所 underwater pump
WO2020111186A1 (en) * 2018-11-30 2020-06-04 株式会社鶴見製作所 Underwater pump
JP2020084952A (en) * 2018-11-30 2020-06-04 株式会社鶴見製作所 Submerged pump
WO2021013782A1 (en) * 2019-07-23 2021-01-28 KSB SE & Co. KGaA Pump assembly comprising a lubrication- and cooling system
CN114127424A (en) * 2019-07-23 2022-03-01 Ksb股份有限公司 Pump device with lubricating and cooling system
US11898570B2 (en) 2019-07-23 2024-02-13 KSB SE & Co. KGaA Pump assembly comprising a lubrication—and cooling system
US11359645B2 (en) 2020-03-17 2022-06-14 Garrett Transportation I Inc Compressor with cooled air passage and liquid coolant passage in axial heat exchanger arrangement
EP3882468A1 (en) * 2020-03-17 2021-09-22 Garrett Transportation I Inc. Compressor with cooled air passage and liquid coolant passage in axial heat exchanger arrangement
US11913473B2 (en) 2020-03-17 2024-02-27 Garrett Transportation I Inc Compressor with electric motor coolant jacket having radial and axial portions
DE202020104824U1 (en) 2020-08-20 2021-11-26 K.H. Brinkmann GmbH & Co Kommanditgesellschaft Medium-cooled liquid pump

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