EP3371465B1 - 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
EP3371465B1
EP3371465B1 EP16787374.4A EP16787374A EP3371465B1 EP 3371465 B1 EP3371465 B1 EP 3371465B1 EP 16787374 A EP16787374 A EP 16787374A EP 3371465 B1 EP3371465 B1 EP 3371465B1
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EP
European Patent Office
Prior art keywords
coolant pump
pump
coolant
control
internal combustion
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
EP16787374.4A
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German (de)
English (en)
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EP3371465A1 (fr
Inventor
Stephan Zielberg
Michael-Thomas Benra
Andreas Burger
Martin Nowak
Stefan Rothgang
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
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Pierburg GmbH
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Publication of EP3371465A1 publication Critical patent/EP3371465A1/fr
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027Varying behaviour or the very pump
    • F04D15/0038Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/10Pumping liquid coolant; Arrangements of coolant pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00Pumping installations or systems
    • F04D13/12Combinations of two or more pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/10Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105Using two or more pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00Control
    • F05D2270/60Control system actuates means
    • F05D2270/64Hydraulic actuators

Definitions

  • the invention relates to a coolant pump for an internal combustion engine having a drive shaft, a coolant pump impeller which is at least rotationally fixed on the drive shaft and via which coolant is conveyed, an adjustable control slide, via a free cross-section of an annular gap between an outlet of the coolant pump impeller and the surrounding conveyor channel is controllable, a control pump with a Regelpumpenlaufrad, which is at least rotationally fixed on the drive shaft, a flow channel of the control pump in which by rotation of the Regelpumpenlaufrades a pressure can be generated, a pressure channel through which an outlet of the flow channel with a first pressure chamber of the control slide fluidly is connectable, which is formed on the side facing away from the coolant pump impeller axial side of the control slide, and a valve, via which a flow cross-section of the pressure channel closable and releasable i st.
  • 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.
  • a pressure side of the secondary pump is closed by a 3/2-way valve in a first position and a suction side of the pump connected to the cooling circuit and the slider and connected in a second position, the pressure side with the slide and the suction side with the cooling circuit.
  • a spring which may possibly be waived by a reset of the pump should be made by the resulting negative pressure on the suction port.
  • a coolant pump in which a hydraulic actuator has a plurality of circumferentially separate pressure chambers through which a rotation is generated.
  • the pressure ring which is actuated by these pressure chambers, is connected via a transmission with the control slide of the coolant pump, which converts the rotational movement of the pressure ring into a translatory movement of the control slide.
  • the flow channel is fluidly connected via a connecting channel with a second pressure chamber of the control slide, which is formed on the pointing to the coolant pump impeller axial side of the control slide, in case of failure of the valve and thus closed connection to the first pressure chamber on the opposite side of the control slide
  • a second pressure chamber of the control slide which is formed on the pointing to the coolant pump impeller axial side of the control slide, in case of failure of the valve and thus closed connection to the first pressure chamber on the opposite side of the control slide
  • the valve is a 3/2-way solenoid valve, which is easy to control and has a small footprint, so that integration into the housing of the coolant pump is possible. By controlling the valve this can be moved to intermediate positions, which also lead according to the shared cross-section to a complete position control of the control slide.
  • control pump impeller is formed integrally with the coolant pump impeller. Accordingly, both wheels can be manufactured and assembled in one manufacturing step. In addition, the required axial space is reduced.
  • the flow channel of the control pump is arranged in a first fixed housing part, on the axially opposite to the flow channel side of the second pressure chamber is formed.
  • This housing part serves at the same time as the axial boundary of the second pressure chamber and the flow housing of the control pump.
  • this housing part can serve as a sliding surface and thus guide for the control slide.
  • the connecting channel is formed in the fixed, the flow channel having housing part. This can be done by forming a simple bore, so that no additional lines between the flow channel and the second pressure chamber must be mounted. The manufacture and assembly of the coolant pump and their space requirements are reduced accordingly.
  • a reliable function in the control of the slide results when the connecting channel extends from a region of an inlet of the control pump in the second pressure chamber.
  • the Regelpumpenlaufrad is at the rear of the coolant pump impeller axially between the second pressure chamber and the coolant pump impeller arranged.
  • this also short flow paths for connecting the pressure chambers with the delivery channel or the impeller of the control pump are created.
  • control pump is a side channel pump, so that the delivery channel can be arranged axially opposite to the impeller. This is particularly suitable for generating high discharge pressures at low flow rates.
  • the pressure channel extends from the outlet of the control pump through the first housing part and a second housing part to the first pressure chamber, wherein in the second housing part of the controlled by the valve flow area is formed.
  • the pressure channel in the first housing part is formed radially inside the control slide and the first housing part bounds the two pressure chambers radially inward.
  • the first housing part can thus simultaneously serve as the inner guide of the control slide.
  • the channels can be made very short, whereby the reaction time of the control is reduced.
  • coolant pump for an internal combustion engine in which the control slide is purely hydraulic, both in normal operation and in the case of the emergency operation, so that no additional components, such as springs and the like are required, sufficient promotion of coolant to prevent overheating to provide the internal combustion engine. Furthermore, only a very small space is required for this pump.
  • the coolant pump according to the invention is also easy 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 a coolant is sucked in via an axial pump inlet 14 which is likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 and formed in the outer housing 10 is conveyed into a cooling circuit of the internal combustion engine.
  • 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.
  • a control pump impeller 22 is formed, which is rotated in accordance with the coolant pump impeller 20.
  • This control pump impeller 22 has blades 23 which are arranged axially opposite to a flow channel 24 formed as a side channel, which is formed in a first inner housing part 26.
  • a Regulating pump 32 forms, via which the pressure of the coolant from the inlet to the outlet 30 is increased.
  • the pulley 36 is mounted on a double-row ball bearing 38, the outer ring 40 is pressed on the pulley 36 and the inner ring 42 on a second inner housing part 44.
  • the second housing part 44 has an inner axial passage opening 46 into which an annular projection 48 of the first housing part 26 protrudes, via which the first housing part 26 is fastened to the second housing part 44.
  • the second housing part 44 is fastened to the outer housing 10 with the interposition of a seal 50.
  • the outer housing 10 at its pump inlet 14 opposite axial end has a receiving opening 52 into which an annular projection 54 of the second housing part 44 protrudes, on the peripheral wall of a groove 56 is formed, in which the seal 50 is arranged.
  • This projection 54 also serves as a rear stop for a control slide 58, the cylindrical peripheral wall 60 can be pushed over the coolant pump impeller 20 so that a free cross section of an annular gap 62 between an outlet 64 of the coolant pump impeller 20 and the delivery channel 12 is controlled. In accordance with the position of this control slide 58, the coolant flow conveyed through the coolant circuit is thus regulated.
  • the control slide 58 has, in addition to the peripheral wall 60, a bottom plate 66 with an inner opening 68, from the outer periphery of which the peripheral wall 60 axially through an annular gap 70 between the first housing part 26 and the outer housing 10 in the direction of axially adjacent annular gap 62 extends.
  • a radial groove 72, 74 is formed in each of which a piston ring 76, 78 is arranged, via which the control slide 58 in the radially inner region on the first housing part 26 and in the radially outer region in the receiving opening 52 of the outer housing 10 is slidably mounted.
  • a first pressure chamber 80 axially through the second housing part 44 and the bottom plate 66 of the control slide 58 and radially outwardly through the outer housing 10 and the annular projection 54 of the second housing part 44 and is bounded radially inwardly by the first housing part 26.
  • a second pressure chamber 82 is formed, which is axially bounded by the bottom plate 66 and the first housing part 26, radially outwardly through the peripheral wall 60 of the control slide 58 and radially inwardly through the first housing part 26 , Depending on the pressure difference applied to the bottom plate 66 of the control slide 58 in the two pressure chambers 80, 82, the peripheral wall 60 of the control slide 58 is correspondingly pushed into or out of the annular gap 62 into the annular gap 62.
  • the pressure difference required for this purpose is generated by the control pump 32 and supplied to the respective pressure chamber 80, 82 by means of a valve 84, which is designed as a 3/2-way solenoid valve.
  • a receiving opening 86 for the valve 84 is formed in the second housing part 44, via which, depending on the position of its closing body 88, a flow cross-section 90 of a pressure channel 92 is regulated.
  • This pressure channel 92 extends from the outlet 30 of the flow channel 24 of the control pump 32 initially into a radially inner region of the first housing part 26 and from there axially into the second housing part 44, in the controllable flow cross-section 90 of the pressure channel 92 is formed, which is closable and releasable by the closing body 88 of the solenoid valve 84. From this controllable flow cross-section 90, the pressure channel 92 extends further into the first pressure chamber 80.
  • the second pressure chamber 82 is connected via a connecting channel 94, which is formed in the first housing part 26, with the flow channel 24, said connecting channel 94 formed by a bore is that extends from a region of the inlet from the flow channel 24 directly into the second pressure chamber.
  • a third, not shown, flow connection of the control valve leads to the suction side of the coolant pump.
  • the annular gap 62 at the outlet 64 of the coolant pump impeller 20 is fully released by the solenoid valve 84 is not energized, whereby the closing body 88 is moved due to a spring force in its the flow cross-section 90 of the pressure channel 92 occlusive position , As a result, no pressure is built up by the coolant in the first pressure chamber 80, but the coolant present in the pressure chamber 80 can flow to the pump inlet 14 of the coolant pump via the not shown other flow connection of the solenoid valve 84, which is released in this state.
  • the control pump 32 promotes against the closed flow cross-section 90, whereby an increased pressure builds up in the entire flow channel 24, which also acts in the region of the inlet of the control pump and correspondingly builds up via the connecting channel 94 in the second pressure chamber 82.
  • This increased pressure in the second pressure chamber 82 has the result that a pressure difference arises on the bottom plate 66 of the control slide 58, which results in that the control slide 58 is displaced into its position releasing the annular gap 62 and thus a maximum delivery the coolant pump is ensured.
  • the control slide 58 In case of failure of the electrical supply of the solenoid valve 84, the control slide 58 assumes the same position, so that a maximum delivery of the coolant pump is ensured in this emergency mode, without the need for a return spring or other, non-hydraulic force would be necessary.
  • An excessive increase of the pressure in the second pressure chamber 82 is avoided, inter alia, by a leakage over the gap 70 between the first housing part 26 and the peripheral wall 60, so that the additionally funded by the control pump 32 coolant is also used for promotion in the cooling circuit.
  • the coolant from the first pressure chamber can flow off via a return duct, not shown, which extends from the solenoid valve 84 through the second housing part 44 and then along the drive shaft 18 in the interior of the first housing part 26 and leads via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump ,
  • the solenoid valve 84 is energized, whereby the closing body 88 releases the flow cross-section 90 of the pressure channel 92. Accordingly, the pressure arising at the outlet 30 of the control pump 32 is also generated in the pressure channel 92 and in the first pressure chamber 80, while at the same time the pressure in the second pressure chamber 82 decreases, since in the region of the inlet by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 82 is initially aspirated.
  • valve 84 it is also possible to move the valve 84 in intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 58, so that complete regulation of the flow cross-section of the annular gap 62 is made possible.
  • the coolant pump described is extremely compact, but easy and inexpensive to produce and assemble.
  • On additional lines for hydraulic connection of the control 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.
  • An adjustment of the control slide is done exclusively on the prevailing in the two pressure chambers hydraulic forces !, So that can be dispensed with additional components, such as return springs. Nevertheless, a reliable emergency operation is ensured, since in case of failure of the energization always a pressure difference across the control slide is created, which shifts this in his the annular gap releasing position.
  • the adjustment in the annular gap closing position of the control slide power requirement is reduced by eliminating the return spring, so that a faster adjustment with smaller cross sections is possible.

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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)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (10)

  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,
    une tirette de réglage (58) 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) entourant peut être réglée,
    une pompe à débit variable (32) avec une roue (22) de la pompe à débit variable, disposée sur l'arbre d'entrainement (18) au moins d'une manière solidaire en rotation,
    un canal d'écoulement (24) de la pompe à débit variable (32) dans lequel une pression peut être générée par rotation de la roue (22) de la pompe à débit variable,
    un canal de pression (92) par lequel une sortie (30) du canal d'écoulement (24) peut être raccordée fluidiquement à une première chambre de pression (80) de la tirette de réglage (58), la chambre étant formée sur la côté axiale de la tirette de réglage (58) détournée de la roue (20) de la pompe à liquide de refroidissement,
    une soupape (84) par laquelle une section d'écoulement (90) du canal de pression (92) peut être fermée et libérée,
    caractérisée en ce que
    le canal d'écoulement (24) est en liaison fluidique avec une deuxième chambre de pression (82) de la tirette de réglage (58) à travers un canal de liaison (94), ladite chambre étant formée sur la côté axiale de la tirette de réglage (58) tournée vers la roue (20) de la pompe à liquide de refroidissement.
  2. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 1, caractérisée en ce que la soupape (84) est une soupape magnétique à 3/2 voies.
  3. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 1 ou 2, caractérisée en ce que la roue (22) de la pompe à débit variable est formée d'un seul tenant avec la roue (20) de la pompe à liquide de refroidissement.
  4. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal d'écoulement (24) de la pompe à débit variable (32) est formé dans une première partie de carter (26) fixe, la deuxième chambre de pression (82) étant disposée sur la côté de ladite partie de carter axialement opposée au canal d'écoulement (24).
  5. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 4, caractérisée en ce que le canal de liaison (94) est formé dans la partie de carter (26) fixe présentant le canal d'écoulement (24).
  6. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal de liaison (94) s'étend depuis une région d'une entrée de la pompe à débit variable (32) dans la deuxième chambre de pression (82).
  7. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que la roue (22) de la pompe à débit variable est disposée sur l'arrière de la roue (20) de la pompe à liquide de refroidissement axialement entre la deuxième chambre de pression (82) et la roue (20) de la pompe à liquide de refroidissement.
  8. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisée en ce que la pompe à débit variable (32) est une pompe à canal latéral.
  9. 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 (92) s'étend depuis la sortie )30) de la pompe à débit variable (32) à travers la première partie du carter (26) et une deuxième partie de carter (44) dans ladite première chambre de pression (80), la section d'écoulement (90) commandée par la soupape (84) étant formée dans la deuxième partie de carter (44).
  10. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 9, caractérisée en ce que le canal de pression (92) est formé dans la première partie de carter (26) radialement à l'intérieur de la tirette de réglage (58), et la première parte de carter (26) délimite les deux chambres de pression (80, 82) radialement vers l'intérieur.
EP16787374.4A 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne Active EP3371465B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119095.8A DE102015119095B4 (de) 2015-11-06 2015-11-06 Kühlmittelpumpe für eine Verbrennungskraftmaschine
PCT/EP2016/075082 WO2017076649A1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3371465A1 EP3371465A1 (fr) 2018-09-12
EP3371465B1 true EP3371465B1 (fr) 2019-11-27

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Application Number Title Priority Date Filing Date
EP16787374.4A Active EP3371465B1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Country Status (6)

Country Link
US (1) US10731654B2 (fr)
EP (1) EP3371465B1 (fr)
JP (1) JP6632721B2 (fr)
CN (1) CN108350889B (fr)
DE (1) DE102015119095B4 (fr)
WO (1) WO2017076649A1 (fr)

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CN108350889B (zh) 2020-10-13
EP3371465A1 (fr) 2018-09-12
US20180320693A1 (en) 2018-11-08
JP6632721B2 (ja) 2020-01-22
WO2017076649A1 (fr) 2017-05-11
US10731654B2 (en) 2020-08-04
CN108350889A (zh) 2018-07-31
DE102015119095B4 (de) 2019-03-21
JP2018532944A (ja) 2018-11-08
DE102015119095A1 (de) 2017-05-11

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