EP3371460B1 - Pompe à liquide de refroidissement destinée au secteur de l'automobile - Google Patents

Pompe à liquide de refroidissement destinée au secteur de l'automobile Download PDF

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Publication number
EP3371460B1
EP3371460B1 EP16741314.5A EP16741314A EP3371460B1 EP 3371460 B1 EP3371460 B1 EP 3371460B1 EP 16741314 A EP16741314 A EP 16741314A EP 3371460 B1 EP3371460 B1 EP 3371460B1
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EP
European Patent Office
Prior art keywords
coolant pump
channel
housing part
side channel
automotive industry
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.)
Active
Application number
EP16741314.5A
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German (de)
English (en)
Other versions
EP3371460A1 (fr
Inventor
Stephan Zielberg
Michael-Thomas Benra
Stefan Rothgang
Andreas Burger
Helmut Prinz
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.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
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Publication date
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Publication of EP3371460A1 publication Critical patent/EP3371460A1/fr
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Publication of EP3371460B1 publication Critical patent/EP3371460B1/fr
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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
    • 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 sector with a drive shaft, a coolant pump impeller which is at least rotatably mounted on the drive shaft and via which coolant in a conveying channel surrounding the coolant pump impeller 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 side channel pump with a sokanalpumpenlaufrad which is rotatably mounted on the drive shaft, a side channel of the side channel pump in which by rotation of the 10%kanalpumpenlaufrades a pressure can be generated, wherein the side channel has 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 secondary pump acting as a secondary pump is from the DE 10 2012 207 387 A1 known.
  • 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 side channel of the side channel pump is arranged, which is arranged correspondingly opposite to the arranged on the shaft side channel pump impeller.
  • a second side 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
  • this wall can be used as a guide for the control slide between the pressure generating coolant flow and the flow rate of the main pump.
  • 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.
  • 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. Furthermore, such an inner guide causes a very exact axial movement, without jerking or tilting of the control slide is to be feared, as always a sufficiently long guide surface is available despite the low space used.
  • 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, there is a smooth gap-free sliding surface.
  • 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 bores in the housing fluidly connected to the side channel of the pump.
  • the pressure channel extends from the outlet of the side channel pump through the first housing part and a second housing part in the first pressure chamber, wherein formed in the second housing part of the valve controlled flow cross-section.
  • the control valve in the housing can also be arranged accordingly, so that here additional connections to the valve omitted.
  • the annular projection of the first housing part at its axial end on a shoulder, from which extends the annular projection of reduced diameter further 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.
  • the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.
  • 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 mounted radially on the inside of the conveying channel 12 on a drive shaft 18, which is designed as a radial impeller, by the rotation of the promotion of the coolant 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 control slide 28 In order to operate this control slide 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 Rare Kanalpumpenankhamrad 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 passage 74 is provided, which serves as a fail-safe hole, as this pressure in the space 64, a pressure is provided which is always greater than the suction pressure of the side channel pump 56.
  • the pressure channel 72 extends from the outlet 54 of the side 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, the pressure channel 72 extends further into the first pressure chamber 58.
  • the connecting channel 74 extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64.
  • This connecting channel 74 is located approximately in the middle, approximately at 150 ° to the inlet 52, between this and the outlet 54.
  • the connecting channel 74 thus acts as a fail-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 is greater than the intake pressure of the side channel pump 56 and thus also the coolant pump 2 in any case, 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
  • 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.
  • This increased pressure in the second pressure chamber 64 has the result that at the bottom 42 of the control slide 28, a pressure difference arises, which causes the control slide 28 is moved to its annular gap 30 releasing position and thus a maximum delivery of the coolant pump 2 is ensured.
  • the control slide 28 In case of failure of the electrical supply of the solenoid valve 66, the control slide 28 correspondingly assumes the same position, so that even in this emergency operation, a maximum delivery of the coolant pump 2 is ensured without the need for a return spring or other, non-hydraulic force would be necessary.
  • 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.
  • the solenoid valve 66 is energized, whereby the closing body 68 releases the flow area 70 of the pressure channel 72 and the flow area between the first pressure chamber 58 and the not shown Return channel reduces or closes. Accordingly, 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. In this state, a correspondingly opposite to the other position of the solenoid valve 66 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 the first housing part 40 with an annular projection 80, the reduced diameter from the annular projection 38 further in from Coolant pump impeller remote end extends, is pushed into a radially inner receiving opening 82 of the second housing part 62 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. In this position, the first housing part 40 is fastened by means of screws 86 on the second housing part. For this purpose, a plurality of through holes 88 and in the second housing part opposite threaded blind holes 90 are formed in the first housing part.
  • the outer housing 10 For attachment of the two housing parts 40, 62 on the outer housing 10 and consequent to the arrangement of the control slide 28 in the outer housing 10, the outer housing 10 at its pump inlet 14 opposite axial end an opening 92 into which an annular projection 94 of the second housing part 62 such protrudes that the projection 94 abuts against the inner wall of the opening 92.
  • an axial groove 96 Radial outside of this hollow cylindrical projection 94, 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 20 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 guided in accordance with sealing.
  • 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 parts.

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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)

Claims (14)

  1. Pompe à liquide de refroidissement destinée au secteur automobile, comprenant un arbre d'entrainement (18), une roue (20) de la pompe à liquide de refroidissement qui est disposée sur l'arbre d'entrainement (18) au moins d'une manière solidaire en rotation et par laquelle de liquide de refroidissement peut être refoulé dans un canal de refoulement (12) entourant ladite roue (20) de la pompe à liquide de refroidissement, une tirette de réglage (28) ajustable par laquelle une section d'écoulement d'une fente annulaire (30) entre une sortie (32) de la roue (20) de la pompe à liquide de refroidissement et le canal de refoulement (12) peut être réglée, une pompe de canal latéral (56) avec une roue (46) de la pompe de canal latéral, disposée sur l'arbre d'entrainement (18) au moins d'une manière solidaire en rotation, un canal latéral (50) de la pompe de canal latéral (56) dans lequel une pression peut être générée par rotation de la roue (46) de la pompe de canal latéral, le canal latéral comprenant une entrée (52) et une sortie (54),
    un canal de pression (72) par lequel la sortie (54) du canal latéral (50) peut être raccordé fluidiquement à une première chambre de pression (58) de la tirette de réglage (28), une soupape (66) par laquelle une section d'écoulement (70) du canal de pression (72) peut être fermée et libérée, caractérisée en ce qu'un canal de liaison (74) depuis le canal latéral (50) à une deuxième chambre de pression (64) est prévu entre l'entrée (52) et la sortie (54), la deuxième chambre de pression (64) étant prévue sur une côté de la tirette de réglage (28) tournée vers ladite roue (20) de la pompe à liquide de refroidissement.
  2. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 1, caractérisée en ce que le canal de liaison (74) est réalisé sous forme d'un alésage.
  3. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 1 ou 2, caractérisée en ce que le canal de liaison est disposé environ au milieu entre l'entrée (52) et la sortie (54).
  4. Pompe à liquide de refroidissement destinée au secteur automobile selon l'une quelconque des revendications 1 à 2, caractérisée en ce que la roue (20) de la pompe à liquide de refroidissement est formée d'un seul tenant avec la roue (46) de la pompe de canal latéral, et le canal latéral (50) est formé dans une première partie de carter (40) sur laquelle ladite tirette de réglage (28) est guidée de manière glissable.
  5. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 4, caractérisée en ce que les palettes (48) de la roue (46) de la pompe de canal latéral sont formées sur l'arrière de la roue (20) de la pompe à liquide de refroidissement réalisée sous forme d'une roue de pompe radiale, qu'elles sont disposées axialement opposées à un canal latéral (50).
  6. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 4 ou 5, caractérisée en ce que la deuxième chambre de pression est prévue entre un fond (42) de la tirette de réglage (28) et une première partie de carter (40) dans laquelle le canal latéral (50) est prévu.
  7. Pompe à liquide de refroidissement destinée au secteur automobile selon l'une quelconque des revendications 4 à 6, caractérisée en ce qu'une paroi de délimitation (78) radiale extérieure du canal latéral (50) s'étend axialement vers la roue (20) de la pompe à liquide de refroidissement, entoure la roue (46) de la pompe de canal latéral radialement et est entourée radialement par une paroi périphérique (44) radiale de la tirette de réglage (28).
  8. Pompe à liquide de refroidissement destinée au secteur automobile selon l'une quelconque des revendications 4 à 7, caractérisée en ce que la première chambre de pression (58) est formée sur la côté axiale de la tirette de réglage (28) détournée de la roue (20) de la pompe à liquide de refroidissement.
  9. Pompe à liquide de refroidissement destinée au secteur automobile selon l'une quelconque des revendications 4 à 8, caractérisée en ce que la tirette de réglage (28) est guidée de manière glissable sur une face extérieure (36) d'une saillie (38) annulaire de la première partie de carter (40), qui s'étend dans la direction axiale.
  10. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 9, caractérisée en ce que la saillie (38) annulaire de la première partie de carter (40) délimite les deux chambres de pression (58, 64) vers l'intérieur radial.
  11. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 9 ou 10, caractérisée en ce que le canal de pression (72) s'étend à travers la saillie annulaire (38) de la première partie de carter (40).
  12. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 11, caractérisée en ce que le canal de pression (72) s'étend de la sortie (54) de la pompe de canal latéral (56) à travers la première partie de carter (40) et une deuxième partie de carter (62) dans la première chambre de pression (58), la section d'écoulement (70) commandée par la soupape (56) étant formée dans la deuxième partie (62).
  13. Pompe à liquide de refroidissement destinée au secteur automobile selon l'une quelconque des revendications 9 à 12, caractérisée en ce que la saillie annulaire (38) de la première partie de carter (40) comprend un épaulement (84) à son extrémité axiale, depuis lequel la saillie annulaire (80) continue, avec un diamètre réduit, dans la direction axiale pour aboutir dans une ouverture de logement (82) de la deuxième partie de carter (62) sur lequel la première partie de carter (40) est montée.
  14. Pompe à liquide de refroidissement destinée au secteur automobile selon la revendication 13, caractérisée en ce que la première partie de carter (40) est fixée sur la deuxième partie de carter (62) per des vis (86).
EP16741314.5A 2015-11-06 2016-07-21 Pompe à liquide de refroidissement destinée au secteur de l'automobile Active EP3371460B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119097.4A DE102015119097B4 (de) 2015-11-06 2015-11-06 Kühlmittelpumpe für eine Verbrennungskraftmaschine
PCT/EP2016/067372 WO2017076524A1 (fr) 2015-11-06 2016-07-21 Pompe à liquide de refroidissement destinée au secteur de l'automobile

Publications (2)

Publication Number Publication Date
EP3371460A1 EP3371460A1 (fr) 2018-09-12
EP3371460B1 true EP3371460B1 (fr) 2019-11-13

Family

ID=56497775

Family Applications (2)

Application Number Title Priority Date Filing Date
EP16741314.5A Active EP3371460B1 (fr) 2015-11-06 2016-07-21 Pompe à liquide de refroidissement destinée au secteur de l'automobile
EP16782281.6A Active EP3371461B1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP16782281.6A Active EP3371461B1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Country Status (6)

Country Link
US (2) US10982676B2 (fr)
EP (2) EP3371460B1 (fr)
JP (2) JP6574311B2 (fr)
CN (2) CN108350886B (fr)
DE (1) DE102015119097B4 (fr)
WO (2) WO2017076524A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015119098B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Regelanordnung für eine mechanisch regelbare Kühlmittelpumpe einer Verbrennungskraftmaschine
DE102015119097B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine
DE102016222288A1 (de) * 2016-11-14 2018-05-17 Mahle International Gmbh Pumpeneinrichtung
KR101881029B1 (ko) * 2017-03-17 2018-07-25 명화공업주식회사 워터펌프
WO2019042530A1 (fr) * 2017-08-29 2019-03-07 Pierburg Pump Technology Gmbh Pompe à liquide de refroidissement pour un moteur à combustion interne
WO2020147936A1 (fr) * 2019-01-15 2020-07-23 Pierburg Pump Technology Gmbh Pompe à liquide de refroidissement de véhicule à moteur mécanique commutable
DE102019123646B4 (de) * 2019-09-04 2023-08-03 Schaeffler Technologies AG & Co. KG Kühlmittelregler mit einem Wellendichtring
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Publication number Publication date
US10982676B2 (en) 2021-04-20
EP3371461B1 (fr) 2019-11-27
US20180320692A1 (en) 2018-11-08
WO2017076524A1 (fr) 2017-05-11
JP2018537609A (ja) 2018-12-20
CN108291550A (zh) 2018-07-17
WO2017076645A1 (fr) 2017-05-11
JP2018530706A (ja) 2018-10-18
CN108350886B (zh) 2020-03-03
JP6574311B2 (ja) 2019-09-11
JP6679718B2 (ja) 2020-04-15
US10508650B2 (en) 2019-12-17
EP3371460A1 (fr) 2018-09-12
EP3371461A1 (fr) 2018-09-12
US20180320695A1 (en) 2018-11-08
CN108291550B (zh) 2021-06-08
DE102015119097A1 (de) 2017-05-11
DE102015119097B4 (de) 2019-03-21
CN108350886A (zh) 2018-07-31

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