EP3371462B1 - 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
EP3371462B1
EP3371462B1 EP16784874.6A EP16784874A EP3371462B1 EP 3371462 B1 EP3371462 B1 EP 3371462B1 EP 16784874 A EP16784874 A EP 16784874A EP 3371462 B1 EP3371462 B1 EP 3371462B1
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EP
European Patent Office
Prior art keywords
coolant pump
circumferential wall
internal combustion
combustion engine
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.)
Active
Application number
EP16784874.6A
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German (de)
English (en)
Other versions
EP3371462A1 (fr
Inventor
Stefan Rothgang
Sebastian Cramer
Michael-Thomas Benra
Andreas Burger
Stephan Zielberg
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 date
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Publication of EP3371462A1 publication Critical patent/EP3371462A1/fr
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Publication of EP3371462B1 publication Critical patent/EP3371462B1/fr
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    • 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

Definitions

  • the invention relates to a coolant pump for an internal combustion engine with a drive shaft, a coolant pump impeller which is arranged at least in a rotationally fixed manner on the drive shaft and via which coolant can be conveyed, an outer housing in which a conveying channel of the coolant pump is formed and an adjustable control slide via which a flow cross section of a Annular gap between an outlet of the coolant pump impeller and the surrounding delivery channel can be regulated.
  • Such coolant pumps are used in internal combustion engines to regulate the amount of coolant delivered in order to prevent the internal combustion engine from overheating. These pumps are mostly driven by a belt or chain drive so that the coolant pump wheel is driven at the speed of the crankshaft or a fixed ratio to the speed of the crankshaft.
  • the amount of coolant delivered must be adapted to the coolant requirements of the internal combustion engine or the motor vehicle.
  • the engine's cold-running phase should be shortened. This takes place, among other things, in that the coolant flow is throttled or completely switched off during this phase.
  • the DE 10 2004 054 637 B4 discloses a controllable coolant pump with an electrically operated control slide, on the outer circumference of which a groove is formed with a piston ring arranged therein, which runs on an inner sliding surface of an outer housing of the electromagnet, so that the slide is supported over this surface.
  • a slide In the radially inner area there is only a line routing over webs on an outside of a hollow cylindrical part of the slide element, which extends in the direction of the electromagnet and serves as an armature.
  • Such a slide is unsuitable for a hydraulically controlled pump, however, since it is not tight in the radially inner area.
  • the bearing surface is very short in the extended position of the slide, so that tilting or blocking, in particular due to penetrating dirt particles, cannot be ruled out, especially since the inner guidance takes place via the webs in an axially distant area.
  • a coolant pump in which the delivery rate of the pump can be changed via an adjustable control slide.
  • This slide is operated either hydraulically or via a scissor mechanism.
  • the force for resetting the slide is provided by a spring element which acts on the slide.
  • the slide is guided via an inner hollow cylindrical section of the slide.
  • the task is therefore to create a coolant pump for an internal combustion engine in which an exact guidance of the control slide is guaranteed in all positions. This should also minimize leaks, so that the control slide for purely hydraulically operated control slide valves can be used on coolant pumps.
  • the frictional forces that occur should be minimized in order to reduce the necessary actuating forces and tightness should be achieved.
  • the available force application areas for hydraulic actuation should be made as large as possible to reduce the necessary pressures,
  • control slide has an inner hollow cylindrical circumferential wall and an outer hollow cylindrical circumferential wall which can be moved into the annular gap, which are connected to one another via a base and extend from the base in the direction of the coolant pump impeller, the inner hollow cylindrical circumferential wall on a machined outer surface a cylindrical section of a housing part of the coolant pump is mounted and the outer hollow cylindrical circumferential wall is guided on a machined inner surface of an axially extending annular projection of a housing part of the coolant pump, an exact inner guidance is ensured, which ensures in every position of the control slide over a sufficiently long guide section becomes.
  • the friction values are low due to the machined inner surfaces.
  • an outer guide is produced in the outer area of the control slide, through which the wear is reduced, for example by penetrating dirt particles. Furthermore, a separation that minimizes leakage can be achieved between the pressure spaces on the front and on the rear of the slide.
  • the outer hollow cylindrical circumferential wall of the control slide has a first axial section which slides within the annular projection and has a shoulder, from which the outer hollow cylindrical circumferential wall extends with an enlarged outer circumference in the direction of the coolant pump impeller.
  • a clearance fit is formed between the section of the outer circumferential wall, the diameter of which is larger, and the surrounding housing, so that on the one hand direct contact with the unmachined inner surface is avoided, which would lead to significantly higher actuating forces due to friction and on the other hand, the existing gaps between the housing and the control slide are minimized.
  • the outer diameter of this section with an enlarged diameter corresponds essentially to the outer diameter of the axially extending annular projection of the housing part.
  • the outer housing into which the coolant pump is inserted can correspondingly have a receiving opening with a constant diameter and the gaps for reducing the leakage can nevertheless be reduced.
  • the shoulder rests axially against one end of the annular projection of the housing part. In this way, the control slide can be prevented from getting stuck due to adhesive forces between the rear wall and the bottom of the slide and the retracted position of the slide can still be clearly defined.
  • a radial groove is provided on the radially inner side of the radially inner circumferential wall formed, in which a sealing ring is arranged, which is advantageously made of polytetrafluoroethylene and correspondingly has a high sliding ability and high corrosion resistance to known coolants such as glycol.
  • a radial groove, in which a sealing ring is arranged, is preferably formed on the radially outer side of the section of the radially outer circumferential wall with a smaller diameter.
  • This is also preferably made of PTFE, so that the tightness is also increased and the friction is reduced in the outer guide area.
  • a leakage flow between the front of the slide and its rear side is minimized accordingly, which reduces a creeping pressure equalization that occurs between the spaces in front of and behind the slide.
  • the actuating forces to be used are correspondingly low.
  • the floor separates a first pressure space from a second pressure space.
  • the two pressure chambers are sealed off from the other pressure chamber by the two sealing rings so that the control slide can be moved depending on a pressure difference between the two pressure chambers without pressure equalization occurring. Due to the low friction due to the good guidance and storage, different positions of the control slide can be approached with low pressure differences to be applied. At the same time, pressure equalization between the pressure chambers is reduced by the high level of tightness via the control slide.
  • a coolant pump for an internal combustion engine is thus created in which the control slide is guided very precisely, which reduces the frictional forces that occur, so that only low actuating forces are required to regulate the coolant flow.
  • large force application areas are made available for the hydraulic adjustment of the control slide.
  • the pressure rooms are very much well sealed against each other both in the inner area and in the outer area of the slide, so that only a minimized leakage flow can arise.
  • Figure 1 shows a side view of a coolant pump according to the invention in a sectional illustration.
  • the coolant pump consists of an outer housing 10 in which a spiral-shaped delivery channel 12 is formed, in which a coolant is sucked in via an axial pump inlet 14 also formed in the outer housing 10, which coolant is drawn in 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.
  • This outer housing 10 can, for example, be designed in one piece with the crankcase or the cylinder head of an internal combustion engine and therefore usually has an inner surface that is not machined, but only a cast inner surface.
  • a coolant pump impeller 20 which is designed as a radial pump wheel, is fastened radially inside the feed channel 12 on a drive shaft 18.
  • a regulating pump impeller 22 is formed, which is rotated accordingly with the coolant pump impeller 20.
  • This regulating pump impeller 22 has blades 23 which are arranged axially opposite one another in the form of a side channel 24, which is formed in a first inner housing part 26.
  • an inlet (not shown) and an outlet (also not shown) are formed, so that the control pump impeller 22 with the flow channel 24 forms a control pump 28, via which the pressure of the coolant is increased from the inlet of the control pump 28 to the outlet.
  • the coolant pump impeller 20 and the regulating pump impeller 22 are driven by a belt of the internal combustion engine, which is rotated with the crankshaft of the internal combustion engine and engages a belt wheel 30 which is attached to the axial end of the drive shaft 18 opposite to the coolant pump impeller 20.
  • the belt wheel 30 is mounted via a two-row ball bearing 32, the outer ring 34 of which is pressed onto the belt wheel 30 and the inner ring 36 of which is pressed onto a second stationary housing part 38.
  • the second housing part 38 has an inner axial through opening 40 through which the drive shaft 18 protrudes with a shaft seal 42 in between and into which an inner annular projection 44 of the first housing part 26 protrudes, via which the first housing part 26 is centered on the second housing part 38.
  • the first housing part 26 is fastened to the second housing part 38 via screws 46 which axially penetrate the first housing part 26.
  • the second housing part 38 is fastened to the outer housing 10 with a seal 48 in between.
  • the outer housing 10 has, at its axial end opposite the pump inlet 14, a receiving opening 50 of constant diameter, into which an annular projection 52 of the second housing part 38 protrudes, a groove 56 on its delimiting flange-shaped wall 54, which rests axially against the outer housing 10 is formed, in which the seal 48 is arranged.
  • an axially displaceable control slide 58 is arranged within the receiving opening 50, the radially outer hollow cylindrical circumferential wall 60 of which can be pushed over the coolant pump impeller 20, 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 regulated.
  • the control slide 58 has an axially shorter inner hollow cylindrical peripheral wall 66 which is connected to the outer peripheral wall 60 via a bottom 68 closed between the peripheral walls 60, 66.
  • the two circumferential walls 60, 66 extend from the base 68 in the direction of the pump impeller 20.
  • the control slide 58 is supported according to the invention via a radial inside 70 of the hollow cylindrical inner circumferential wall 66, which is axially on a machined outer surface 72 of a cylindrical section 74 of the first housing part 26 is sliding.
  • the outer surface 72 is machined to a mean roughness value of approximately 0.3 ⁇ m, as a result of which a very low-friction mounting is achieved.
  • This inner bearing ensures very precise guidance of the control slide 58, by means of which tilting or tilting of the control slide 58 is reliably avoided even when pressures are applied.
  • the radially outer circumferential wall 60 has a first section 76 which extends axially from the bottom 68 and which slides with its radial outer side 78 on a mechanically machined inner surface 80 of the annular projection 52 and has a smaller outer diameter than a second section adjoining the first section 76 Section 82 of the outer circumferential wall 60, the outer diameter of which corresponds approximately to the outer diameter of the annular projection 52 and which can be displaced into the annular gap 62.
  • the circumferential wall 60 has a shoulder 84 from which the circumferential wall 60 with the enlarged diameter extends further axially in the direction of the annular gap 62 and with which the circumferential wall 60 in the fully retracted position against an end 86 of the annular projection 52 is applied so that this end 86 serves as a rear stop for the control slide 58.
  • the second section 82 of the circumferential wall 60 lies directly opposite an inner wall 88 of the receiving opening 50 of the outer housing 10, a clearance fit being selected between the inner wall 88 and the radial outer side 78 of the second section 82 of the circumferential wall 60, which minimizes the gaps in this area will.
  • a radial groove 90 is formed on the outside 78, in which a sealing ring 92 is arranged, which is preferably made of PTFE.
  • the sealing ring 92 is arranged in such a way that it rests against the machined inner surface 80 of the annular projection 52 of the second housing part 38 in every position of the control slide 58, so that this sealing ring 92 also achieves a good and long-lasting seal in addition to the low-friction and precise guidance through which leakage between the protrusion 52 and the outer peripheral wall 60 is minimized.
  • a radial groove 94 is also formed on the radial inner side 70 of the radially inner circumferential wall 66, in which a sealing ring 96 is also arranged, which is preferably made of PTFE, which is insensitive to the coolant and has good sliding properties.
  • a first pressure chamber 98 is formed on the side of the control slide 58 facing away from the coolant pump impeller 20, which is axially through the second housing part 38 and the bottom 68 of the control slide 58 and radially outward through the annular projection 52 of the second housing part 38 and radially inward the cylindrical section 74 of the first housing part 26 serving as a bearing surface is delimited and on the side of the bottom 68 facing the coolant pump impeller 20 a second pressure chamber 100 is formed, which is axially through the bottom 68 and the first housing part 26 and radially outward through the peripheral wall 60 of the control slide 58 and is again limited radially inward by the section 74 of the first housing part 26.
  • the outer circumferential wall 60 of the regulating slide 58 is pushed into or out of the annular gap 62 accordingly, so that to avoid pressure equalization between the two pressure chambers 98 , 100 the pressure chambers 98, 100 must be tightly sealed to one another, which is achieved on the one hand by the exact mounting and guidance of the control slide 58 and on the other hand by the sealing rings 92, 96.
  • the pressure difference necessary to adjust the control slide 58 is generated by the control pump 28 and fed to the respective pressure chamber 98, 100 by means of a valve 102, which is designed as a solenoid valve.
  • a valve 102 which is designed as a solenoid valve.
  • correspondingly arranged channels not visible in the figures are formed in the two housing parts 26, 38, via which pressurized coolant can be supplied to the respective pressure chamber 98, 100 or can be drained from it, so that the control slide valve as a result of this pressure difference 58 is pushed into the annular gap 62 to minimize the amount of coolant conveyed or pushed out of the annular gap 62 to maximize the amount of coolant conveyed into the cooling circuit.
  • the coolant pump described has a very precise and low-friction inner bearing and additional outer guidance, so that despite small gaps, only small actuating forces are required, which is reinforced by the good sliding properties of the sliding surfaces opposite the peripheral walls.
  • the long-lasting and easy-to-slide sealing rings used are additionally sealed against one another, so that the control slide can be adjusted with low actuating forces and pressure equalization between the pressure chambers is delayed.
  • large force application areas are made available on the bottom of the control slide for its hydraulic adjustment. Guiding over unmachined surfaces in the area of the receiving opening of the outer housing is avoided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (9)

  1. Pompe à liquide de refroidissement pour moteur à combustion interne comprenant
    un arbre d'entraînement (18),
    une roue de pompe à liquide de refroidissement (20) disposée au moins de manière fixe en rotation sur l'arbre d'entraînement (18) et par laquelle le liquide de refroidissement peut être refoulé,
    un carter extérieur (10) dans lequel est formé un canal de refoulement (12) de la pompe de refroidissement,
    un coulisseau de commande réglable (58), par lequel une section transversale d'écoulement d'un espace annulaire (62) entre une sortie (64) de la roue de pompe de liquide de refroidissement (20) et le canal de refoulement environnant (12) peut être réglée,
    caractérisé en ce que
    le coulisseau de commande (58) présente une paroi (66) périphérique cylindrique creuse intérieure et une paroi périphérique (60) cylindrique creuse extérieure, chacune pouvant être déplacé dans l'espace annulaire (62), lesdites parois étant reliées l'une à l'autre via une base (68) et s'étendent depuis la base (68) vers la roue de pompe de liquide de refroidissement (20), la paroi (66) périphérique cylindrique creuse intérieure étant montée sur une surface (72) extérieure usinée d'une section cylindrique (74) d'une partie du carter (26) de la pompe de liquide de refroidissement, et la paroi (60) périphérique cylindrique creuse externe est guidée sur une surface (80) interne usinée d'une saillie annulaire s'étendant axialement (52) d'une partie de carter (38) de la pompe de refroidissement.
  2. Pompe à liquide de refroidissement pour un moteur à combustion interne selon la revendication 1, caractérisé en ce que la paroi (60) circonférentielle cylindrique creuse externe présente une première section axiale (76) qui coulisse à l'intérieur de la saillie annulaire (52) et présente un épaulement (84) à partir duquel la paroi (60) circonférentielle cylindrique creuse externe s'étend dans une deuxième section (82) avec une circonférence extérieure élargie vers la roue de pompe de liquide de refroidissement (20).
  3. Pompe à liquide de refroidissement pour un moteur à combustion interne selon la revendication 2, caractérisé en ce qu'un ajustement de jeu est formé entre la section (82) de la paroi (60) périphérique extérieure, dont le diamètre est plus grand, et le carter (10) extérieur environnant.
  4. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une des revendications 2 ou 3, caractérisé en ce que le diamètre extérieur de la partie (82) de la paroi (60) circonférentielle extérieure ayant un diamètre élargi correspond sensiblement au diamètre extérieur de la saillie (52) annulaire s'étendant axialement de la partie du carter (38).
  5. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une des revendications précédentes 2 à 4, caractérisé en ce qu'en position complètement rétractée du coulisseau de commande (58), l'épaulement (84) repose axialement sur une extrémité (86) de la saillie annulaire (52) de la partie du carter (38).
  6. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une rainure radiale (94), dans laquelle est disposée une bague d'étanchéité (96), est formée sur un côté (70) radialement intérieur de la paroi (66) circonférentielle radialement intérieure.
  7. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes et la revendication 2, caractérisé en ce qu'une rainure radiale (90) est formée sur un côté extérieur radial (78) de la première section (76) de la paroi (60) circonférentielle radialement extérieure (60) de plus petit diamètre, dans laquelle rainure une bague d'étanchéité (92) est agencée.
  8. Pompe à liquide de refroidissement pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisé en ce que la base (68) sépare une première chambre de pression (98) d'une deuxième chambre de pression (100), de sorte que le coulisseau de commande (58) peut être déplacé en fonction d'une différence de pression entre les deux chambres de pression (98, 100).
  9. Pompe à liquide de refroidissement pour moteur à combustion interne selon la revendication 8, caractérisé en ce que chacune des deux chambres de pression (98, 100) est scellée de l'autre chambre de pression (98, 100) par les deux bagues d'étanchéité (92, 96).
EP16784874.6A 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne Active EP3371462B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119089.3A DE102015119089B4 (de) 2015-11-06 2015-11-06 Kühlmittelpumpe für eine Verbrennungskraftmaschine
PCT/EP2016/075077 WO2017076646A1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3371462A1 EP3371462A1 (fr) 2018-09-12
EP3371462B1 true EP3371462B1 (fr) 2020-12-02

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ID=57184441

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16784874.6A Active EP3371462B1 (fr) 2015-11-06 2016-10-19 Pompe à liquide de refroidissement pour un moteur à combustion interne

Country Status (3)

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EP (1) EP3371462B1 (fr)
DE (1) DE102015119089B4 (fr)
WO (1) WO2017076646A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE881306C (de) * 1941-10-28 1953-06-29 Voith Gmbh J M Kreiselpumpe mit Spaltringschuetze

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4070132A (en) * 1976-11-02 1978-01-24 Baltimore Aircoil Company, Inc. Variable performance pump
DE102004054637B4 (de) 2004-11-12 2007-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102008026218B4 (de) * 2008-05-30 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102009048349B3 (de) * 2009-10-06 2010-11-18 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Kühlmittelpumpe
DE102011079898A1 (de) 2011-07-27 2013-01-31 Mahle International Gmbh Pumpe
DE102012207387A1 (de) * 2011-07-27 2013-01-31 Mahle International Gmbh Kühleinrichtung
DE102013018205B3 (de) * 2013-10-30 2014-06-18 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE881306C (de) * 1941-10-28 1953-06-29 Voith Gmbh J M Kreiselpumpe mit Spaltringschuetze

Also Published As

Publication number Publication date
WO2017076646A1 (fr) 2017-05-11
DE102015119089A1 (de) 2017-05-11
EP3371462A1 (fr) 2018-09-12
DE102015119089B4 (de) 2019-03-21

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