EP3371460A1 - Coolant pump for the automotive industry - Google Patents
Coolant pump for the automotive industryInfo
- Publication number
- EP3371460A1 EP3371460A1 EP16741314.5A EP16741314A EP3371460A1 EP 3371460 A1 EP3371460 A1 EP 3371460A1 EP 16741314 A EP16741314 A EP 16741314A EP 3371460 A1 EP3371460 A1 EP 3371460A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- coolant pump
- housing part
- pressure
- coolant
- 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.)
- Granted
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 103
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 239000010881 fly ash Substances 0.000 claims description 2
- 238000002485 combustion reaction Methods 0.000 description 9
- 238000001816 cooling Methods 0.000 description 5
- 230000001419 dependent effect Effects 0.000 description 5
- 238000009434 installation Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 229910052761 rare earth metal Inorganic materials 0.000 description 2
- 150000002910 rare earth metals Chemical class 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- BUGBHKTXTAQXES-UHFFFAOYSA-N Selenium Chemical compound [Se] BUGBHKTXTAQXES-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910052711 selenium Inorganic materials 0.000 description 1
- 239000011669 selenium Substances 0.000 description 1
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
- 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
- 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
-
- 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
- F04D13/12—Combinations of two or more 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
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
-
- 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
- F01P2003/001—Cooling 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
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P2005/105—Using two or more pumps
-
- 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 a coolant pump for the motor vehicle area with a drive shaft, a coolant pump impeller, which is arranged at least rotatably on the drive shaft and via which coolant in a surrounding the coolant pump impeller conveyor channel is conveyed, an adjustable control slide, via which a flow cross-section of an annular gap between a Outlet of the coolant pump impeller and the delivery channel is controllable, a Rare channel pump with a sokanalpumpenlaufrad which is rotatably mounted on the drive shaft is at least one side channel of the side channel pump in which by rotation of the 10%kanalpumpenlaufrades a pressure can be generated, the Rare channel having an inlet and an outlet, a pressure channel, via which the outlet of the side channel is fluidically connectable to a first pressure chamber of the control slide, and a valve, via which a flow cross section of the pressure channel versc can be left and released.
- Such coolant pumps serve, for example, in internal combustion engines to regulate the quantity of the delivered coolant in order to prevent overheating of the internal combustion engine.
- the drive of these pumps is usually via a belt or chain drive, so that thedeffenpumpenrad is driven by the speed of the crankshaft or a fixed ratio to the speed of the crankshaft.
- the amount of coolant conveyed to the coolant requirement of the internal combustion engine or the motor vehicle adapt.
- the cold running phase of the engine should be shortened. This is done, inter alia, by throttling or completely shutting off the coolant flow during this phase.
- Such a coolant device with a lateral pump acting as a secondary pump is known from DE 10 2012 207 387 AI.
- This pump is located at the back of the pump, a slider which is displaceable by a pressure in an annular chamber and can be reset by a spring.
- This annular chamber is formed in a housing, which in turn is arranged on the back of the slide and in which a first Rare channel of the side channel pump is arranged, which is arranged correspondingly opposite to the arranged on the shaft Rare channel pump impeller.
- a second rare-earth channel is formed in a further housing part.
- a pressure side of the side channel pump is closed in this pump in a first position and a suction side of the pump connected to the cooling circuit and the slider and in a second position, the pressure side with the annular chamber of the slide and the suction side with the cooling circuit connected.
- a detailed channel and flow guidance is not disclosed.
- the flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort.
- the connecting channel is designed as a bore.
- the connecting channel is arranged approximately centrally between the inlet and the outlet.
- the connecting channel thus acts as a fail-safe device, which ensures that when the solenoid valve in each Operating situation of the full volume flow of the coolant pump is provided.
- the exact positioning of the connection channel is dependent on the pressure gradient in the side channel.
- the coolant pump impeller is formed integrally with the side channel pump impeller and the side channel is formed in a first housing part on which the control slide is slidably guided.
- the axial length required is considerably shortened.
- the first housing part takes over both the function as a flow housing and as a storage for the slide, so that short pressure channels can be realized.
- the blades of the side channel pump impeller are formed on a back side of the coolant pump impeller formed as a radial pump impeller and are arranged axially opposite to a side channel.
- the purely axial alignment of the side channel to the blading reduces the required radial space, since no radially outer overflow channel is needed. Accordingly, a maximum pressure can be generated to the available space.
- a radially outer boundary wall of the side channel extends axially in the direction of the coolant pump impeller, surrounds the side channel pump impeller radially and is surrounded radially by a radially outer peripheral wall of the control slide.
- This wall fills in accordance with the gap between the slider and the rotating side channel pump impeller and thus between the pressure generating coolant flow and the flow of the main pump.
- this wall can be used as a guide for the control slide.
- control slide is slidably guided on an outer surface of an annular, axially extending projection of the first housing part.
- This projection is correspondingly formed in the radially inner region of the first housing part and correspondingly allows an inner bearing of the control slide on the advantageously machined outer surface.
- this outer surface may also have a coating.
- This inner bearing of the control slide simplifies installation in a receiving opening of a cylinder crankcase, the inner surfaces then do not need to be edited.
- such an inner guide causes a very exact axial movement, without any fear of tilting or tilting of the control slide, as always a sufficiently long guide surface is available despite the small space used.
- the first pressure chamber is formed on the axial side of the control slide facing away from the coolant pump impeller.
- the adjustment of the control slide can be done completely in accordance with hydraulic forces, which are supplied only to the corresponding pressure chambers. Additional annular spaces or piston chambers need not be formed.
- the fluidic connection to the pressure chambers can be made due to the limitation by the first housing part via a simple bore in this housing part, so that additional lines are not required.
- the annular projection of the first housing part bounds the two pressure chambers radially inward. Additional Seals in this area are not required accordingly. Furthermore, a smooth gap-free sliding surface results.
- the pressure channel extends through the annular projection of the first housing part, so that no further lines are to be mounted here, but also the first pressure chamber can be connected directly via the holes in the housing fluidly with the side channel of the pump.
- the pressure channel from the outlet of the rare-earth pump extends through the first housing part and a second housing in the first pressure chamber, wherein in the second housing part of the valve controlled flow cross-section is formed.
- the annular projection of the first housing part at its axial end on a shoulder, from which the annular projection of reduced diameter further extends axially into a corresponding receiving opening of the second housing part to which the first housing part is fixed.
- the inner projection a direct centering of the two housing parts to each other, whereby the recording and management of the control slide is improved.
- This can be manufactured with small tolerances, so that a high tightness along the slide with good double-sided leadership is achievable.
- a particularly simple and releasable attachment results when the first housing part is fastened by means of screws on the second housing part.
- a coolant pump for the motor vehicle area is created in which, due to the axial arrangement of the individual cell relative to one another, a significantly reduced axial [suction space is required.
- the pump is easy to assemble, eliminating the need for extra lines and fewer components.
- the pump has a high reliability because the slider has a reliable guidance and storage. Accordingly, the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.
- FIG. 1 shows a side view of a coolant pump according to the invention in a sectional view
- FIG. 2 is a sectional view of a rare view of the coolant pump according to the invention rotated relative to FIG. 1;
- FIG. 3 shows a front view cut in the region of a side channel pump of the coolant pump
- Figure 4 is a rotated to Figure 1 partial view of the coolant pump according to the invention in a sectional view.
- a coolant pump 2 consists of an outer housing 10, in which a spiral conveying channel 12 is formed, into which a coolant is sucked via an axial pump inlet 14 likewise formed in the outer housing 10, which coolant flows via the conveying channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and is conveyed into a cooling circuit of an internal combustion engine.
- This outer housing 10 can In particular, be formed by a cylinder crankcase, which has a recess for receiving the remaining coolant pump.
- a coolant pump impeller 20 is fixed radially inside the conveying channel 12 on a drive shaft 18, which is designed as Radialpumpenrad, by the rotation of the promotion of the coolant takes place in the conveying channel 12.
- the pulley 24 is supported by a double row ball bearing 26.
- a drive via a chain drive would also be possible.
- a control slide 28 is used, which is displaceable into an annular gap 30 between an outlet 32 of the coolant pump impeller 20 and the surrounding delivery channel 12 and regulates according to the available flow cross section.
- the control slide 28 is slidably mounted via an inner, hollow cylindrical peripheral wall 34 on a mechanically machined outer surface 36 of an annular, axially extending projection 38 of a first inner housing part 40.
- This inner peripheral wall 34 extends from a bottom 42 of the control slide 28 concentric with a radially outer peripheral wall 44, which also extends in the same direction from the bottom 42 and is displaced into the annular gap 30 for flow control.
- this Reschi discard 28 is at the pump inlet 14 opposite axial side of the Coolant pump impeller 20 integrally formed with the coolant pump impeller 20, a side channel pump impeller 46 which is driven in accordance with the coolant pump impeller 20.
- This This iskanalpumpencroftrad 46 has blades 48 which are arranged axially opposite to a side channel 50 which is formed in the first inner housing part 40, from which also in the radially inner region of the annular projection 38 for supporting the control slide 28 to the coolant pump impeller 20 opposite side extends axially.
- an inlet 52 and an outlet 54 are formed, so that the side channel pump impeller 46 with the axially opposite side channel 50 forms a side channel pump 56, via which the pressure of the coolant from the inlet 52 to the outlet 54 of the side channel pump 56 is increased.
- the conveyed through the side channel pump 56 coolant which generates a hydraulic pressure can now either a first pressure chamber 58 are supplied, which on the side facing away from the coolant pump impeller 20 side of the control slide 28 between the bottom 42 of the control slide 28 and a pad 60 of a second housing part 62nd is formed or returned via a solenoid valve 66 of the coolant pump 2.
- a second pressure chamber 64 which is arranged between the bottom 42 of the control slide 28 and the first housing part 40, there is a speed-dependent hydraulic pressure.
- a receptacle 65 for the valve 66 is provided with respect to the pressure chamber 58 in the second housing part 62, which serves as a 3/2-way solenoid valve is formed and has a connection to the pressure chamber 58, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled.
- a Connecting channel 74 is provided, which serves as a fail-safe hole, as a pressure is thereby provided in the pressure chamber 64, which is always greater than the suction pressure of the side channel pump 56 Is.
- the pressure channel 72 extends from the outlet 54 of the selenium channel 50 of the side channel pump 56 first into a radially inner region of the first housing part 40, which forms the annular projection 38 and from there axially into the second housing part 62, in which the controllable flow cross-section 70 of the pressure channel 72nd is formed, which is closed by the closing body 68 of the solenoid valve 66 and releasable. From this controllable flow cross section 70 extends the pressure channel 72 further into the first pressure chamber 58th
- the second pressure chamber 64 is connected to the side channel 50 via the connecting channel 74, which is formed in the first housing part 40, this connecting channel 74 being directly from a region of the inlet 52 from the side channel 50 extends into the second pressure chamber 64.
- This connecting channel 74 is located approximately in the center, at approximately 150 ° to the inlet 52, between this and the outlet 54.
- the connecting channel 74 thus acts as a case-safe device, which ensures that when switched off or disturbed solenoid valve 66 in any operating situation In the pressure chamber 64 a speed-dependent pressure prevails, which in any case is greater than the suction pressure of the side channel pump 56 and thus also the coolant pump 2, since this pressure yes prevails in the first pressure chamber 58.
- the exact positioning of the connecting channel is dependent on the pressure gradient in the side channel 50.
- a third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump. 2 If the coolant pump 2 in tietrieb promote a maximum amount of coolant, the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is fully released by the solenoid valve 66 is not energized, whereby the closing body 68 moved due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position becomes.
- the coolant from the first pressure chamber 58 can flow off via a return channel, not shown, extending from the solenoid valve 66 through the second housing part 62 and then along the drive shaft 18 in the interior of the first housing part 40 and via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump 2 leads. If a reduced coolant flow torison Vietnamese Republiciauf demanded by the engine control, as is the case for example during the cold running phase, the solenoid valve 66 is energized, whereby the closing body 68, the flow area 70 of the pressure channel 72 releases and the flow cross-section between the first pressure chamber 58 and the not shown Return channel reduces or closes.
- the pressure arising at the outlet 54 of the side channel pump 56 is also supplied through the pressure channel 72 to the first pressure chamber 58 in order to displace the control slide 28 into the annular gap 30.
- a corresponding opposite to the other position of the solenoid valve 66 opposite pressure difference at the bottom 42 of the control slide 28, which causes the control slide 28 is moved into the annular gap 30 and thus the coolant flow is interrupted in the cooling circuit.
- valve 66 If a controllable solenoid valve 66 is used, it is also possible to move the valve 66 in intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 28, so that complete regulation of the flow cross-section of the annular gap 30 is made possible.
- the first housing part 40 is attached directly to the second housing part 62. This is done by mounting the first housing 40 with an annular projection 80 of reduced diameter from the annular protrusion 38 in the housing In a radially inner receiving opening 82 of the second housing part 62 is pushed until the first housing part 40 abuts with its formed between the projections 38, 80 paragraph 84 against the pad 60 of the second housing part 62.
- the first housing part 40 is fastened by means of screws 86 on the second housing part.
- a plurality of through holes 88 and in the second Gesimousetefl opposite threaded blind holes 90 are formed in the first housing part.
- an axial groove 96 is formed, in which a sealing ring 98 is arranged, which is pressed correspondingly in the attachment of the second housing part 62 on the outer housing 10, wherein the second housing part 62 with its connection surface 60 against an outer wall 100 of the outer housing 10 is present.
- This projection 94 also serves as a rear stop 102 for the control slide 28, the outer peripheral wall 44 continues with its pointing to the coolant pump impeller 44 end with a slightly larger diameter.
- a radial groove 104, 106 is formed, in each of which a piston ring 108, 110 is arranged, via which the control slide 28 in the radially inner region on the projection 38 of the first housing part 26 and in the radial outer region on an inner wall of projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 is slidably mounted and correspondingly guided sealingly.
- the coolant pump 2 described is extremely compact, but easy and inexpensive to produce and assemble, since a small number of parts is present.
- On additional lines for hydraulic connection of the side channel pump with the pressure chambers of the control slide can be omitted, since they can be formed over very short distances as simple holes in the two inner housing cells.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015119097.4A DE102015119097B4 (en) | 2015-11-06 | 2015-11-06 | Coolant pump for an internal combustion engine |
PCT/EP2016/067372 WO2017076524A1 (en) | 2015-11-06 | 2016-07-21 | Coolant pump for the automotive industry |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3371460A1 true EP3371460A1 (en) | 2018-09-12 |
EP3371460B1 EP3371460B1 (en) | 2019-11-13 |
Family
ID=56497775
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16741314.5A Active EP3371460B1 (en) | 2015-11-06 | 2016-07-21 | Coolant pump for the automotive industry |
EP16782281.6A Active EP3371461B1 (en) | 2015-11-06 | 2016-10-19 | Coolant pump for an internal combustion engine |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16782281.6A Active EP3371461B1 (en) | 2015-11-06 | 2016-10-19 | Coolant pump for an internal combustion engine |
Country Status (6)
Country | Link |
---|---|
US (2) | US10982676B2 (en) |
EP (2) | EP3371460B1 (en) |
JP (2) | JP6574311B2 (en) |
CN (2) | CN108350886B (en) |
DE (1) | DE102015119097B4 (en) |
WO (2) | WO2017076524A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015119098B4 (en) * | 2015-11-06 | 2019-03-21 | Pierburg Gmbh | Control arrangement for a mechanically controllable coolant pump of an internal combustion engine |
DE102015119097B4 (en) * | 2015-11-06 | 2019-03-21 | Pierburg Gmbh | Coolant pump for an internal combustion engine |
DE102016222288A1 (en) * | 2016-11-14 | 2018-05-17 | Mahle International Gmbh | pump means |
KR101881029B1 (en) * | 2017-03-17 | 2018-07-25 | 명화공업주식회사 | Waterpump |
DE112017007961A5 (en) * | 2017-08-29 | 2020-07-09 | Pierburg Pump Technology Gmbh | Coolant pump for an internal combustion engine |
WO2020147936A1 (en) * | 2019-01-15 | 2020-07-23 | Pierburg Pump Technology Gmbh | Switchable mechanical motor vehicle coolant pump |
DE102019123646B4 (en) * | 2019-09-04 | 2023-08-03 | Schaeffler Technologies AG & Co. KG | Coolant regulator with a shaft seal |
JP7215379B2 (en) * | 2019-09-19 | 2023-01-31 | トヨタ自動車株式会社 | engine cooling system |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
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US3364860A (en) | 1966-09-01 | 1968-01-23 | Gorman Rupp Ind Inc | Combined recirculating and drain pump construction |
JPS51119604U (en) * | 1975-03-26 | 1976-09-28 | ||
JPS51119604A (en) | 1975-04-14 | 1976-10-20 | Shin Etsu Chem Co Ltd | A method and apparatus for melting low melting point metals using wast e tires as fuel |
SE469040B (en) | 1991-09-03 | 1993-05-03 | Flygt Ab Itt | CENTRIFUGAL PUMP WHEEL FOR PUMP INTENDED TO PUMP WATER SHOES CONTAINING SOLID PARTICLES |
DE4318158A1 (en) | 1992-08-10 | 1994-02-17 | Volkswagen Ag | Coolant pump for vehicle IC engine - has vented leakage chamber with lead-off channel to suction side of pump |
DE19826902C2 (en) * | 1998-06-17 | 2000-05-04 | Mannesmann Vdo Ag | Feed pump |
JP2001248442A (en) | 2000-03-02 | 2001-09-14 | Honda Motor Co Ltd | Engine cooling device |
DE102008026218B4 (en) * | 2008-05-30 | 2012-04-19 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Adjustable coolant pump |
DE102008061407B4 (en) | 2008-12-10 | 2013-09-05 | Mtu Friedrichshafen Gmbh | Water pump for coolant delivery in a low-temperature and a high-temperature circuit |
DE102010044167A1 (en) | 2010-11-19 | 2012-05-24 | Mahle International Gmbh | Coolant pump mounted in motor vehicle, has valve device that is provided to disconnect suction side and pressure side of displacement pump which is connected to slider, for adjusting fluid pressure |
EP2455615B1 (en) * | 2010-11-19 | 2017-08-16 | MAHLE International GmbH | Pump |
DE102011012826B3 (en) | 2011-03-02 | 2012-01-12 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for internal combustion engine of motor car, has passage hole arranged between pressure channel and pressure chamber before magnetic valve, where magnetic valve produces defined pressurization of regulating valve |
DE102011001090A1 (en) | 2011-03-04 | 2012-09-06 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod | Controllable cooling system for a motor vehicle, coolant pump therefor, usable in the coolant pump impeller and method for controlling a flow of coolant in such a cooling system |
DE102012207387A1 (en) | 2011-07-27 | 2013-01-31 | Mahle International Gmbh | Cooling device for internal combustion engine in motor car, has pressure relief valve arranged over pressure side of secondary pump and inserted along direction of cooling circuit when reaching pre-defined pressure |
DE102012214503B4 (en) | 2012-08-14 | 2017-10-12 | Schwäbische Hüttenwerke Automotive GmbH | Rotary pump with adjustable delivery volume, in particular for adjusting a coolant pump |
DE102013011209B3 (en) | 2013-07-04 | 2014-01-23 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for internal combustion engine mounted in e.g. truck, has piston rod that is connected with permanent magnet, and linearly moved with respect to solenoid coil |
DE102013111939B3 (en) | 2013-10-30 | 2014-10-30 | Pierburg Gmbh | Coolant pump for use in the automotive sector |
DE102014013224B3 (en) | 2014-09-05 | 2015-07-30 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | control device |
DE102015119097B4 (en) * | 2015-11-06 | 2019-03-21 | Pierburg Gmbh | Coolant pump for an internal combustion engine |
DE102015119095B4 (en) * | 2015-11-06 | 2019-03-21 | Pierburg Gmbh | Coolant pump for an internal combustion engine |
-
2015
- 2015-11-06 DE DE102015119097.4A patent/DE102015119097B4/en active Active
-
2016
- 2016-07-21 JP JP2018519746A patent/JP6574311B2/en active Active
- 2016-07-21 EP EP16741314.5A patent/EP3371460B1/en active Active
- 2016-07-21 US US15/772,813 patent/US10982676B2/en active Active
- 2016-07-21 CN CN201680064591.6A patent/CN108350886B/en active Active
- 2016-07-21 WO PCT/EP2016/067372 patent/WO2017076524A1/en active Application Filing
- 2016-10-19 JP JP2018522763A patent/JP6679718B2/en not_active Expired - Fee Related
- 2016-10-19 US US15/772,817 patent/US10508650B2/en not_active Expired - Fee Related
- 2016-10-19 WO PCT/EP2016/075076 patent/WO2017076645A1/en active Application Filing
- 2016-10-19 CN CN201680063475.2A patent/CN108291550B/en not_active Expired - Fee Related
- 2016-10-19 EP EP16782281.6A patent/EP3371461B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
CN108350886A (en) | 2018-07-31 |
JP2018530706A (en) | 2018-10-18 |
DE102015119097A1 (en) | 2017-05-11 |
US20180320695A1 (en) | 2018-11-08 |
JP6574311B2 (en) | 2019-09-11 |
WO2017076524A1 (en) | 2017-05-11 |
CN108350886B (en) | 2020-03-03 |
CN108291550B (en) | 2021-06-08 |
WO2017076645A1 (en) | 2017-05-11 |
EP3371461A1 (en) | 2018-09-12 |
US20180320692A1 (en) | 2018-11-08 |
US10982676B2 (en) | 2021-04-20 |
US10508650B2 (en) | 2019-12-17 |
CN108291550A (en) | 2018-07-17 |
JP2018537609A (en) | 2018-12-20 |
EP3371461B1 (en) | 2019-11-27 |
DE102015119097B4 (en) | 2019-03-21 |
EP3371460B1 (en) | 2019-11-13 |
JP6679718B2 (en) | 2020-04-15 |
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