EP3371461B1 - Pompe à liquide de refroidissement pour un moteur à combustion interne - Google Patents

Pompe à liquide de refroidissement pour un moteur à combustion interne Download PDF

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Publication number
EP3371461B1
EP3371461B1 EP16782281.6A EP16782281A EP3371461B1 EP 3371461 B1 EP3371461 B1 EP 3371461B1 EP 16782281 A EP16782281 A EP 16782281A EP 3371461 B1 EP3371461 B1 EP 3371461B1
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EP
European Patent Office
Prior art keywords
housing part
coolant pump
side channel
internal combustion
combustion engine
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
EP16782281.6A
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German (de)
English (en)
Other versions
EP3371461A1 (fr
Inventor
Stephan Zielberg
Andreas Burger
Michael-Thomas Benra
Stefan Rothgang
Michael Becker
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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Filing date
Publication date
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Publication of EP3371461A1 publication Critical patent/EP3371461A1/fr
Application granted granted Critical
Publication of EP3371461B1 publication Critical patent/EP3371461B1/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 an internal combustion engine with a drive shaft, a coolant pump impeller, which is at least rotationally fixed on the drive shaft and via which coolant in a surrounding the coolant pump impeller conveyor is conveyed, an adjustable control slide, via which a flow cross section of an annular gap between an outlet of theméffenpumpenlaufrades 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%pumpenlaufrades a pressure can be generated, a pressure channel through which an outlet of the side channel with a first Pressure chamber of the control slide is fluidically connectable, and a valve, via which a flow cross-section of the pressure channel can be closed and released.
  • Such coolant pumps are used in internal combustion engines to control the amount of subsidized 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 pumped coolant quantity is to be adapted to the coolant requirement of the internal combustion engine or of the motor vehicle.
  • Coolant pumps In order not to have to provide the necessary for the process of the slide coolant amount on additional conveyor units, such as additional piston / cylinder units or to compress other hydraulic fluids for actuation, are mechanically controllable Coolant pumps have become known, on the drive shaft, a second delivery wheel is arranged, via which the pressure for adjusting the slide is provided. These pumps are designed, for example, as side channel pumps or servo pumps.
  • 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 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 the gap between the spool and the rotating side channel pump impeller, and thus between the pressure generating refrigerant flow and the main pump flow.
  • this wall can be used as a guide for the control slide.
  • the first pressure chamber is formed on the axial side facing away from the coolant pump impeller of the control slide and the first housing part defines a second pressure chamber to a first axial side and the control slide to the opposite axial side.
  • the adjustment of the control slide can accordingly completely done by hydraulic forces that 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, 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 an annular projection of reduced diameter further extends axially into a corresponding receiving opening of the second housing part, on which the first housing part is fixed. It exists accordingly over 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 connecting channel is formed in the first housing part, which extends from the side channel through the first housing part in the second pressure chamber. This can be made by a short bore or directly during casting. Any additional lines are eliminated and the assembly is facilitated accordingly.
  • the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.
  • the coolant pump consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which via a likewise formed in the outer housing 10 axial pump inlet 14, a coolant is sucked, which via the delivery channel 12 to a formed in the outer housing 10 tangential pump outlet 16 and is conveyed into a cooling circuit of the internal combustion engine.
  • This outer housing 10 may 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 a 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 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.
  • a bykanalpumpenankratrad 46 is formed, which is driven in accordance with the coolant pump impeller 20.
  • 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 hydraulic pressure provided by the side channel pump 56 can now either be supplied to a first pressure chamber 58 which is formed on the side of the control slide 28 facing away from the coolant pump impeller 20 between the bottom 42 of the control slide 28 and a connection surface 60 of a second housing part 62 or one second pressure chamber 64 are fed, between the Bottom 42 of the control slide 28 and the first housing part 40 is arranged.
  • a receptacle 65 for a valve 66 is arranged in the second housing part 62, which is designed as a 3/2-way solenoid valve and a connection to the pressure chambers 58, 64 has, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled.
  • This 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 second pressure chamber 64 is connected via a connecting channel 74, which is formed in the first housing part 40, with the side channel 50, said connecting channel 74 formed by a bore is that extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64.
  • a third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump.
  • the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is fully released by the solenoid valve 66 is energized, whereby the closing body 68 is displaced due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position ,
  • the flow port of the solenoid valve 66 which is released in this state, can flow to the pump inlet 14 of the coolant pump.
  • the side channel pump 56 promotes against the closed flow cross-section 70 of the pressure channel 72, whereby an increased pressure builds up in the entire side channel 50, which also acts in the region of the inlet 52 of the side channel 56 and accordingly in the second pressure chamber via the connecting channel 74 64 builds.
  • 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 displaced in its annular gap 30 releasing position and thus a maximum delivery of the coolant pump is ensured.
  • Too much increase in the pressure in the second pressure chamber 64 is inter alia by leakage through a gap 76 between a side channel 50 radially outwardly delimiting boundary wall 78 of the first housing part 40, which surrounds the sokanalpumpenank 46 immediately, and the radially outer peripheral wall 44 of Control slide 28 avoided, so that the additionally funded by the side channel pump 56 coolant is also used for promotion in the cooling circuit.
  • 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 40th extends and leads via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump.
  • 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, while at the same time the pressure in the second pressure chamber 64 decreases, since in the region of the inlet 52 by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 64 is initially aspirated.
  • valve 66 it is also possible to drive the valve 66 in intermediate positions, whereby for each position of the Regulating slide 28 a balance of forces can be achieved, so that a complete control 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 is pushed with an annular projection 80 which extends from the annular projection 38 farther in the coolant pump impeller farther end remote in a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 with his trained between the projections 38, 80 paragraph 84 abuts 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 in the attachment of the second housing part 62 on the outer housing 10th is pressed accordingly, the second housing part 62 abuts with its connection surface 60 against an outer wall 100 of the outer housing 10.
  • 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 is slidably supported on an inner wall of the projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 and guided sealingly.
  • the coolant pump described is extremely compact, but easy and inexpensive to manufacture 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 (11)

  1. Pompe à liquide de refroidissement pour moteur à combustion interne, 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,
    un canal de pression (72) par lequel une sortie (54) du canal latéral (50) peut être raccordée 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,
    dans laquelle 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 la tirette de réglage (28) est guidée de manière glissante.
  2. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 1, 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, et qu'elles sont disposées axialement opposées à un canal latéral (50).
  3. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 2, 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).
  4. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, 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.
  5. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, 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, et que la première partie de carter (40) délimite une deuxième chambre de pression (64) vers une première côté axiale et que la tirette de réglage (28) la délimite vers la côté axiale opposée.
  6. Pompe à liquide de refroidissement pour moteur à combustion interne selon les revendications 4 et 5, 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.
  7. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal de pression (72) s'étend à travers la saillie annulaire (38) de la première partie de carter (40).
  8. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 7, 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 de carter (62).
  9. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications 4 et 8, 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 une saillie annulaire (80) continue, avec un diamètre réduit, dans la direction axiale pour aboutir dans une ouverture de logement (82) correspondante de la deuxième partie de carter (62) sur lequel la première partie de carter (40) est montée.
  10. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 9, caractérisée en ce que la première partie de carter (40) est fixée sur la deuxième partie de carter (62) par des vis (86).
  11. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un canal de liaison (74) est formé, qui s'étend depuis le canal latéral (50) à travers la première partie de carter (40) dans la deuxième chambre de pression (64).
EP16782281.6A 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne Active EP3371461B1 (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/EP2016/075076 WO2017076645A1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3371461A1 EP3371461A1 (fr) 2018-09-12
EP3371461B1 true EP3371461B1 (fr) 2019-11-27

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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 Before (1)

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

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

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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
JP7215379B2 (ja) * 2019-09-19 2023-01-31 トヨタ自動車株式会社 エンジン冷却装置
WO2022073589A1 (fr) * 2020-10-06 2022-04-14 Pierburg Pump Technology Gmbh Pompe de liquide de refroidissement automobile mécanique variable
US11725616B1 (en) * 2022-03-15 2023-08-15 Delphi Technologies Ip Limited Sealing ring gland and fuel pump including the same

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US10982676B2 (en) 2021-04-20
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
EP3371460B1 (fr) 2019-11-13

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