US20160215679A1 - Adjustable coolant pump - Google Patents

Adjustable coolant pump Download PDF

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Publication number
US20160215679A1
US20160215679A1 US14/915,331 US201414915331A US2016215679A1 US 20160215679 A1 US20160215679 A1 US 20160215679A1 US 201414915331 A US201414915331 A US 201414915331A US 2016215679 A1 US2016215679 A1 US 2016215679A1
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US
United States
Prior art keywords
pump
disposed
slide valve
piston
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/915,331
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English (en)
Inventor
Franz Pawellek
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nidec GPM GmbH
Original Assignee
Nidec GPM GmbH
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 Nidec GPM GmbH filed Critical Nidec GPM GmbH
Assigned to NIDEC GPM GMBH reassignment NIDEC GPM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PAWELLEK, FRANZ
Publication of US20160215679A1 publication Critical patent/US20160215679A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/12—Filtering, cooling, or silencing cooling-air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12—Pump-driving arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0077—Safety measures
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the invention relates to an adjustable coolant pump, particularly for use in internal combustion engines.
  • the cooling output of the coolant pumps must be adapted to these greater engine outputs, so that in the case of engines having an increasing engine output, the related coolant pump must already summon up a correspondingly great conveying output in the lower speed of rotation range, and must be dimensioned to he correspondingly large, and this necessarily requires an increased space requirement in the engine compartment.
  • modules such as heat exchangers, for example, are destroyed, the most varied pressure regulation functions are used.
  • their use in turn requires a further demand for space in the engine compartment, and furthermore often requires auxiliary energies for activation, which energies roust be made available by way of supply lines, which require an even greater demand for space.
  • overpressure protection is implemented by way of bypass lines, for example, wherein such solutions necessarily result in great energy losses.
  • the displacement piston has a conveying pressure applied to it on both sides.
  • the spring space can be relieved of pressure by way of an external valve, thereby initiating an adjustment of the control slide valve in the “open” direction.
  • this embodiment requires very cost-intensive, complex production, and furthermore an external control valve as well as externally conducted drain lines, so that this design requires a great demand for space/construction space.
  • a further significant disadvantage of the design previously described in DE 881 306 B consists in that this solution cannot guarantee the failure safety (fail-safe) that is absolutely required for coolant pumps, because the conveying volume stream is completely closed off if the regulation device fails.
  • the displacement piston sealing surfaces are also not protected against particles entrained by the conveying medium, on the one hand, and on the other hand, the shaft seal is subject to the stress of the full conveying pressure, so that not only the useful lifetime but also the reliability of the pump is greatly restricted.
  • the impeller is furthermore mounted on the shaft in axially displaceable but torque-proof manner.
  • the conveying pressure acts between the pressure slant in the housing and the open impeller, and displaces the impeller counter to the spring force of a plate spring that lies against the rear side of the impeller when a preset value has been reached.
  • the conveying pressure of the pump decreases as a result of the sealing gap relative to the pressure slant becoming larger during this axial displacement of the impeller.
  • a prerequisite for this is that a space (i.e. the spring space) having a lower pressure level as compared with the conveying pressure is present on the rear side of the impeller.
  • the coolant pump requires a relatively large construction space as a consequence of the control unit that can be controlled externally with outside energy, the magnetic coil.
  • the setting element/spring element that “makes do” without outside energy in this solution, and has a pressure regulation function is a plate spring used due to limitations of the construction space, which spring is very greatly restricted in terms of its force/lift ratio, so that the opening pressure can be adjusted only very imprecisely with this solution.
  • control slide valve is disposed on an a spring-loaded, axially displaceable ring piston, wherein the control pressure for activation of the control slide valve is generated by an axial piston pump that lies against the rear wall of the pump wheel, which wall is specifically configured as a slanted disk for this purpose, and adjusted by means of a solenoid valve disposed in the pump housing.
  • a further solution is known from DE 10 2012 207 387 A1, by means of which a valve slide valve spring-loaded by a return spring, once again having a rear wall and an outer cylinder disposed on this rear wall and variable covering the outflow region of the impeller, can be hydraulically adjusted by means of a 3/2-way valve, wherein the hydraulic pressure required for adjustment of the slide valve is generated by a “second” impeller disposed on the pump shaft of the impeller, of a further secondary pump integrated into the housing.
  • the invention is therefore based on the task of developing an infinitely adjustable coolant pump (having a control slide valve), driven by way of an drive wheel, which avoids all the disadvantages of the state of the art mentioned above, furthermore demonstrates clear energy advantages as compared with constant pumps having an overpressure valve, particularly does not require any outside energy (such as hydraulics, vacuum, electrical energy) for pressure or volume stream regulation, guarantees great failure safety (fail-safe), and is supposed to guarantee optimal heating of engines having great engine outputs with reference to the displacement, which require coolant pumps having a large design, and is supposed to influence the engine temperature during long-term operation, in infinite manner, in highly dynamic manner, and very reliably, over very long periods of use, in very precise manner, and, in this regard, at the same time, is supposed to have a minimal construction size that optimally utilizes the construction space present in the engine compartment, wherein the coolant pump to be developed is furthermore supposed to be able to be produced in simple and cost-advantageous manner, in terms of production and installation technology, and is supposed to
  • this task is accomplished by an adjustable coolant pump driven by way of a drive wheel, for internal combustion engines, in accordance with the characteristics of the independent claim of the invention.
  • FIG. 1 the adjustable coolant pump according to the invention, disposed on an engine housing 37 , in a side view, in section;
  • FIG. 2 the pump shaft 4 with the pilot valve 20 in a spatial exploded representation
  • FIG. 3 the detail Z from FIG. 1 with a schematic representation of the “control streams” during the “opening phase” of the control slide valve 12 ;
  • FIG. 4 the detail Z from FIG. 1 with a schematic representation of the “control streams” during the “closing phase” of the control slide valve 12 .
  • FIG. 1 shows the adjustable coolant pump according to the invention, disposed on an engine housing 37 , having a pump housing 1 , a pump shaft 4 mounted on the pump housing 1 in a pump bearing 2 , driven by a drive wheel 3 , here in the design of a pulley 40 , having an impeller 5 disposed in torque-proof manner on a free, flow-side end of this pump shaft 4 , and having a ring piston 7 spring-loaded by a return spring 6 , axially guided in the pump housing 1 , on which piston the rear wall 8 of a control slide valve 12 disposed in the pump interior 9 and having an outer cylinder 11 that variably covers the outflow region 10 of the impeller 5 is rigidly attached, wherein a shaft seal 14 is disposed in a seal accommodation 13 , between the pump shaft 4 and the pump housing 1 , and furthermore, pump mandrels 15 formed by the pump housing 1 or disposed on the pump housing 1 are disposed in the pump interior 9 , on which mandrels a wall disk 16
  • a slide valve guide 17 for the ring piston 7 spring-loaded by the return spring 6 is disposed on the pump housing 1 , which guide guides the ring piston 7 on the outer mantle and, at the same time, is furthermore at a free distance from the pump shaft 4 with its inner mantle.
  • the slide valve guide 17 lies against the wall disk 16 with its free, flow-side end, so that the components that are adjacent to one another, i.e. the slide valve guide 17 , the wall disk 16 , a sealing disk 33 disposed on the inner circumference of the disk, spaced apart from the pump shaft 4 by a throttle gap, radially movable on the wall disk 16 , the pump shaft 4 , and the shaft seal 14 , jointly enclose/form a pressure chamber 18 in the form of a ring cylinder.
  • the sealing disk 33 disposed in the wall disk 16 in radially movable manner, the inside diameter of which has only little play (tight running seat) relative to the outside diameter of the pump shaft 4 , represents a throttle gap that permits only slight leakages into the pressure chamber 18 .
  • one/multiple passage bore(s) 19 is/are disposed in the slide valve guide 17 , at a distance from the wall disk 16 .
  • a pilot valve 20 consisting of a setting screw 22 provided with a central outlet bore 21 , a valve spring 23 , and a valve piston 24 are disposed in a valve seat bore at the impeller-side free end of the pump shaft 4 , in such a manner that the valve piston 24 closes off a shaft bore 25 that opens into the valve seat bore, disposed centrally in the pump shaft 4 , in the closed state of the pilot valve 20 , which shaft bore opens into the pressure chamber 18 by way of one/multiple transverse bore(s) 26 disposed in the pump shaft 4 .
  • the pilot valve 20 , the pump shaft 4 having the pilot shaft 20 are shown in a spatial exploded representation in FIG. 2 .
  • the return spring 6 which lies against the ring piston 7 with one spring end, lies against the spring contact 27 of a filter sleeve 29 provided with laser bores 28 with its other spring end, and presses the sleeve against the wall disk 16 in this regard, forming a seal.
  • the laser bores 28 prevent the entry of any dirt load and thereby increase the reliability of the control apparatus according to the invention.
  • the laser bores 28 in the arrangement according to the invention serve as an inflow aperture and guarantee that the amount of liquid flowing in is not more than can drain away by way of the pilot valve 20 .
  • a filter piston slide valve 30 is rigidly disposed on the ring piston 7 , which valve slides along the outside circumference of the filter sleeve 29 when the ring piston 7 is displaced, and thereby frees the filter sleeve 29 of any dirt load, i.e. cleans the laser bores 28 /(filter bores) disposed in the filter sleeve 29 of the dirt particle accumulations in their inflow region, and thereby guarantees great reliability, even under extreme conditions of use.
  • the ring piston 7 together with the filter piston slide valve 30 , the filter sleeve 29 , the wall disk 16 , and the slide valve guide 17 enclose a spring pressure space 31 in the form of a ring cylinder.
  • a control slide valve seal 32 is disposed on the outside circumference of the wall disk 16 , i.e. toward the outer cylinder 11 , and the sealing disk 33 is disposed on the inside circumference of the wall disk 16 , and as a result, an impeller rear side space 34 disposed in the pump interior 9 , between the pump shaft 4 , the rear wall of the impeller 5 , the wall disk 16 , and the outer cylinder 11 is separated, on the pressure side, from a control slide valve interior 36 disposed between the rear wall 8 , the filter sleeve 29 , the wall disk 16 , and the outer cylinder 11 , wherein the working pressure that is built up in the spiral channel 39 is constantly applied in the control slide valve interior 36 , in that mandrel passages 35 are disposed in the rear wall 8 .
  • FIGS. 1 and 2 the method of functioning/method of action of the coolant pump according to the invention, the structure of which has been explained, will now be discussed using FIGS. 3 and 4 .
  • FIG. 3 shows the detail Z from FIG. 1 with a schematic representation of the “control streams” during the “opening phase” of the control slide valve 12 .
  • the control slide valve 12 moves in the direction of the pulley 40 and, in this regard, opens the outflow region 10 of the impeller 5 with its outer cylinder 11 .
  • a lower pressure is applied to the impeller rear side space 34 (which is sealed off relative to the control slide valve interior 36 ) and to the spring pressure space 31 (which is connected with the control slide valve interior 36 by way of the filter sleeve 29 , provided with laser bores, which acts as a throttle).
  • the same pressure is applied to the valve piston 24 of the pilot valve 20 as directly behind the filter sleeve 29 in the spring pressure space 31 ; this pressure will be referred to as the control pressure in the further explanations.
  • This control pressure engages at the ring surface of the ring piston 7 to which this pressure is applied.
  • the resulting pressure force will be referred to as control pressure force hereinafter.
  • the spring force of the return spring 6 directed in the same direction as this control pressure force, furthermore also engages on the ring piston 7 .
  • control pressure force and the spring force form an opening force that engages on the ring piston 7 .
  • This opening force strives to displace the control slide valve 12 , which is rigidly connected with the ring piston 7 , into the end position on the drive side.
  • a closing pressure force directed counter to the opening force engages at the control slide valve 12 , which force proceeds from the surface to which working pressure is applied at the ring piston 7 .
  • the surfaces of the ring piston 7 (and also of the control slide valve 12 ), to which the working pressure is applied in “opposite” manner, and the effects of which cancel one another out as activations at the control slide valve 12 are left out of account.
  • FIG. 4 shows the detail Z from FIG. 1 with a schematic representation of the control streams of the “closing phase” of the control slide valve 12 .
  • the control slide valve 12 moves in the direction of the impeller 5 and, in this regard, closes off the outflow region 10 of the impeller 5 with its outer cylinder 11 .
  • the filter sleeve 29 continues to also increase as a result of the arrangement according to the invention, with an increasing working pressure, and this pressure, as has already been explained, is applied directly to the valve piston 24 of the pilot valve 20 , the pilot valve 20 can be pre-adjusted when a maximal permissible working pressure is reached, in such a manner that the valve then opens, and, in this regard, the cooling medium situated in the pressure chamber 18 , is emptied into the suction channel 38 , as shown in FIG. 4 .
  • the laser bores 28 in the “inflow aperture,” the filter sleeve 29 are designed/dimensioned, in terms of number and size, in such a manner that the amount of coolant that flows In through the filter sleeve 2 S is not greater than can drain away by way of the pilot valve 20 .
  • pressure relief takes place in the pressure chamber 18 , as well as in the spring pressure space 31 connected with the pressure chamber 18 by way of the passage bore 19 , thereby the control pressure force decreases, and if the spring force remains constant, the opening force therefore decreases below the value of the closing pressure force that is dependent on the respective working pressure, so that the closing pressure force, which is greater relative to the opening force, now brings about displacement of the ring piston 7 (with the control slide valve 12 disposed on it) in the direction of the impeller 5 .
  • the control slide valve 12 closes the outflow region 10 of the impeller 5 off with its outer cylinder 11 , and the working pressure drops.
  • Optimal adjustment of the working pressure which avoids the disadvantages of the state of the art, has clear energy advantages, does not require any outside energy (such as hydraulics, vacuum, electrical energy) for pressure or volume stream control, guarantees great failure safety (fail-safe), and guarantees optimal warm-up of engines at great engine outputs, with reference to the displacement, which outputs require coolant pumps having very large designs, and with which the engine temperature can be adjusted very precisely, even after the engine has warmed up, during long-term operation, in infinite manner, in highly dynamic manner, and very reliably, over very long periods of use, and which simultaneously has a minimal construction size that optimally utilizes the construction space present in the engine compartment, furthermore can be produced in simple manner, in terms of production and installation technology, and in cost-advantageous manner, and which constantly guarantees great operational safety and great reliability over the entire useful lifetime, results from the interplay of the effects of the arrangement according to the invention, as explained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
US14/915,331 2013-10-30 2014-10-22 Adjustable coolant pump Abandoned US20160215679A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE201310018205 DE102013018205B3 (de) 2013-10-30 2013-10-30 Regelbare Kühlmittelpumpe
DE102013018205.0 2013-10-30
PCT/DE2014/000538 WO2015062565A1 (de) 2013-10-30 2014-10-22 Regelbare kühlmittelpumpe

Publications (1)

Publication Number Publication Date
US20160215679A1 true US20160215679A1 (en) 2016-07-28

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Application Number Title Priority Date Filing Date
US14/915,331 Abandoned US20160215679A1 (en) 2013-10-30 2014-10-22 Adjustable coolant pump

Country Status (7)

Country Link
US (1) US20160215679A1 (zh)
EP (1) EP3063412A1 (zh)
JP (1) JP2016535833A (zh)
KR (1) KR20160078365A (zh)
CN (1) CN105874208A (zh)
DE (1) DE102013018205B3 (zh)
WO (1) WO2015062565A1 (zh)

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RU179501U1 (ru) * 2017-07-18 2018-05-16 Федеральное государственное бюджетное образовательное учреждение высшего образования "Астраханский государственный технический университет", ФГБОУ ВО "АГТУ" Механизм поворота лопаток рабочего колеса свободновихревого насоса
US20190186497A1 (en) * 2017-12-18 2019-06-20 Hyundai Motor Company Coolant pump and cooling system provided with the same for vehicle
US10578006B2 (en) 2015-11-06 2020-03-03 Pierburg Gmbh Method for controlling a mechanically controllable coolant pump for an internal combustion engine
US10815865B2 (en) * 2018-03-27 2020-10-27 Hyundai Motor Company Coolant pump and cooling system for vehicle
CN112502998A (zh) * 2020-12-01 2021-03-16 石家庄栾兴泵业有限公司 一种低噪节能的双壳渣浆泵
US11002281B2 (en) 2017-09-01 2021-05-11 Nidec Gpm Gmbh Controllable coolant pump for a main delivery circuit and a secondary delivery circuit
USD923060S1 (en) * 2018-08-09 2021-06-22 Psg Germany Gmbh Pump
RU207994U1 (ru) * 2021-04-21 2021-11-29 Общество с ограниченной ответственностью "Инженерно-технологическая промышленная компания" Насос для системы охлаждения двигателя внутреннего сгорания
US20220099016A1 (en) * 2019-01-15 2022-03-31 Pierburg Pump Technology Gmbh Switchable mechanical motor vehicle coolant pump
USD960203S1 (en) * 2020-09-28 2022-08-09 Hugo Vogelsang Maschinenbau Gmbh Pump for liquids
USD966342S1 (en) * 2020-02-07 2022-10-11 Pedrollo S.P.A. Electric pump
US12018690B2 (en) * 2020-10-06 2024-06-25 Pierburg Pump Technology Gmbh Variable mechanical automotive coolant pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015119089B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine
DE102017126870A1 (de) * 2017-11-15 2019-05-16 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit höhenverstellbarem Kolben und Kupplung mit Nehmerzylinder
KR102474350B1 (ko) * 2017-12-06 2022-12-05 현대자동차 주식회사 냉각수 펌프유닛, 및 이를 구비한 엔진 냉각시스템

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE881306C (de) * 1941-10-28 1953-06-29 Voith Gmbh J M Kreiselpumpe mit Spaltringschuetze
DE102011113040B3 (de) * 2011-09-09 2012-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt "Regelbare Kühlmittelpumpe"
US8297942B2 (en) * 2008-05-30 2012-10-30 Geraete- Und Pumpenbau Gmbh Dr. Eugen Schmidt Regulatable coolant pump
US20130309103A1 (en) * 2012-05-15 2013-11-21 Schaeffler Technologies AG & Co. KG Actuator system for a controlled coolant pump
DE102014009367B3 (de) * 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004054637B4 (de) * 2004-11-12 2007-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102008022354B4 (de) * 2008-05-10 2012-01-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe und Verfahren zu deren Regelung
DE102012207387A1 (de) * 2011-07-27 2013-01-31 Mahle International Gmbh Kühleinrichtung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE881306C (de) * 1941-10-28 1953-06-29 Voith Gmbh J M Kreiselpumpe mit Spaltringschuetze
US8297942B2 (en) * 2008-05-30 2012-10-30 Geraete- Und Pumpenbau Gmbh Dr. Eugen Schmidt Regulatable coolant pump
DE102011113040B3 (de) * 2011-09-09 2012-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt "Regelbare Kühlmittelpumpe"
US9528521B2 (en) * 2011-09-09 2016-12-27 Nidec Gpm Gmbh Controllable coolant pump
US20130309103A1 (en) * 2012-05-15 2013-11-21 Schaeffler Technologies AG & Co. KG Actuator system for a controlled coolant pump
DE102014009367B3 (de) * 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10578006B2 (en) 2015-11-06 2020-03-03 Pierburg Gmbh Method for controlling a mechanically controllable coolant pump for an internal combustion engine
RU179501U1 (ru) * 2017-07-18 2018-05-16 Федеральное государственное бюджетное образовательное учреждение высшего образования "Астраханский государственный технический университет", ФГБОУ ВО "АГТУ" Механизм поворота лопаток рабочего колеса свободновихревого насоса
US11002281B2 (en) 2017-09-01 2021-05-11 Nidec Gpm Gmbh Controllable coolant pump for a main delivery circuit and a secondary delivery circuit
US20190186497A1 (en) * 2017-12-18 2019-06-20 Hyundai Motor Company Coolant pump and cooling system provided with the same for vehicle
US10578113B2 (en) * 2017-12-18 2020-03-03 Hyundai Motor Company Coolant pump and cooling system provided with the same for vehicle
CN108019356A (zh) * 2017-12-28 2018-05-11 湖南泵阀制造有限公司 一种具有调流与截断功能的多功能离心泵及管路系统
US10815865B2 (en) * 2018-03-27 2020-10-27 Hyundai Motor Company Coolant pump and cooling system for vehicle
USD923060S1 (en) * 2018-08-09 2021-06-22 Psg Germany Gmbh Pump
USD941884S1 (en) 2018-08-09 2022-01-25 Psg Germany Gmbh Pump
USD950609S1 (en) * 2018-08-09 2022-05-03 Psg Germany Gmbh Pump
USD952000S1 (en) * 2018-08-09 2022-05-17 Psg Germany Gmbh Engine part
USD968472S1 (en) 2018-08-09 2022-11-01 Psg Germany Gmbh Pump
US20220099016A1 (en) * 2019-01-15 2022-03-31 Pierburg Pump Technology Gmbh Switchable mechanical motor vehicle coolant pump
USD966342S1 (en) * 2020-02-07 2022-10-11 Pedrollo S.P.A. Electric pump
USD960203S1 (en) * 2020-09-28 2022-08-09 Hugo Vogelsang Maschinenbau Gmbh Pump for liquids
US12018690B2 (en) * 2020-10-06 2024-06-25 Pierburg Pump Technology Gmbh Variable mechanical automotive coolant pump
CN112502998A (zh) * 2020-12-01 2021-03-16 石家庄栾兴泵业有限公司 一种低噪节能的双壳渣浆泵
RU207994U1 (ru) * 2021-04-21 2021-11-29 Общество с ограниченной ответственностью "Инженерно-технологическая промышленная компания" Насос для системы охлаждения двигателя внутреннего сгорания

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EP3063412A1 (de) 2016-09-07
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CN105874208A (zh) 2016-08-17
KR20160078365A (ko) 2016-07-04
JP2016535833A (ja) 2016-11-17

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