EP2646693B1 - Pompe de refroidissement - Google Patents

Pompe de refroidissement Download PDF

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Publication number
EP2646693B1
EP2646693B1 EP11811520.3A EP11811520A EP2646693B1 EP 2646693 B1 EP2646693 B1 EP 2646693B1 EP 11811520 A EP11811520 A EP 11811520A EP 2646693 B1 EP2646693 B1 EP 2646693B1
Authority
EP
European Patent Office
Prior art keywords
pump
coolant
impeller
guide
flow
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
EP11811520.3A
Other languages
German (de)
English (en)
Other versions
EP2646693A1 (fr
Inventor
Andreas Schmidt
Franz Pawellek
Toni Steiner
Silvio Bischoff
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.)
Nidec GPM GmbH
Original Assignee
Nidec GPM GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nidec GPM GmbH filed Critical Nidec GPM GmbH
Publication of EP2646693A1 publication Critical patent/EP2646693A1/fr
Application granted granted Critical
Publication of EP2646693B1 publication Critical patent/EP2646693B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/04—Helico-centrifugal 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
    • F04D13/02—Units comprising pumps and their driving means
    • 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
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers

Definitions

  • the invention relates to a mechanical of a pulley, a gear, a stub shaft o.ä. driven coolant pump for internal combustion engines in the design of an axially flowed coolant pump.
  • axially flowed coolant pumps for internal combustion engines are described. These are either by means of electric motor or mechanically eg via pulleys or similar. driven by the crankshaft of the internal combustion engine. So is among other things from the US 6 056 518 A a not provided by a shaft, but by a switched reluctance motor driven, equipped with a Halbaxialerielrad coolant pump described, which is driven by an electric motor Halbaxialflugelrad mounted on its outer circumference in a pump housing with central flow inlet and central flow outlet.
  • the applicant was in the DE 100 47 387 A1 also an already proven in practice, electrically driven, controllable coolant pump for internal combustion engines with a Axialschaufelrad presented in the design of a controllable axially flowed coolant pump.
  • controllable coolant pump for internal combustion engines with axial impellers were also by the applicant in the DE 102 07 653 C1 as well as in the DE 103 14 526 B4 presented.
  • Significant disadvantages of these aforementioned coolant pumps result not least from their drive, and since the electric motors are arranged within the coolant flow, the electric motors used in each case space-constrained always transmitted only limited torques.
  • the inevitably required, waterproof encapsulation of the electric motors inevitably higher production costs.
  • due to the electrical components or electronic components used always comply with upper limits of the temperature load to avoid failure of these components.
  • This coolant pump designed as a controllable axial pump has a hollow shaft driven by a toothed belt pulley, on which a plurality of rotor blades are non-rotatably arranged such that their angle of attack can be adjusted mechanically via a mechanism of action arranged inside the hollow shaft.
  • the actuation of the mechanical Verstellmechanismusses takes place via an actuating element, which can be controlled electrically, electronically, hydraulically or pneumatically.
  • a unilaterally mounted Axialpumpenrad is arranged in a pump housing, wherein the pump has two coolant outlet openings, one of which can be completely closed by means of a arranged after the Axialpumpenrad control element.
  • the in the DE 10 2008 048 893 A1 disclosed solution with a one-sided storage of Axialpumpenrades has the disadvantages that the smallest possible diameter of the pulley is limited by the bearing diameter, and that also the one-sided storage negatively affected the required minimum gap dimensions on Axialpumpenrad, so that due to the design-related, high gap inevitably loss of efficiency must be taken into account.
  • a coolant pump for simultaneous coolant delivery on the one hand in a low-temperature and on the other in a high-temperature circuit, with a low-temperature housing together with low-temperature spiral inside, and a high-temperature housing together with high-temperature spiral inside, with a special coolant pump radial impeller for the simultaneous delivery of coolant into the low-temperature spiral and the high-temperature spiral with a drive shaft for driving the coolant pump radial impeller known.
  • a further coolant pump in a radial construction ie with axial flow inlet, a radial impeller and radial flow outlet known, in which between the drive shaft and the bearing element two rows of rolling elements and a number of sealing arrangements are provided, which effect a seal between the drive shaft and the bearing element.
  • One of the sealing arrangements in this case has a sealing ring which is pressed by elastic means against a back surface of the impeller.
  • axially flowed coolant pumps also an unstable course of the characteristic of the coolant flow over the pump pressure at a constant speed is characteristic, ie if at constant speed (engine speed) a consumer in the coolant circuit partially switched on or off, then changes it the coolant volume flow. Due to the unstable characteristic of these axially flow-through coolant pumps of the prior art, however, this has become very important in the axially flow-through coolant pumps of the prior art adverse impact, sudden, and usually serious change in the respective pump pressure result.
  • the invention is therefore based on the object, a mechanically from a pulley, a gear, a stub shaft o.ä. to develop driven axially flowed coolant pump for internal combustion engines, which avoids the aforementioned disadvantages of the prior art, with respect to the prior art lower installation space / volume and the same, i.
  • FIG. 1 is a possible design of a mechanically driven by a pulley 1, according to the invention axially flowed through coolant pump for internal combustion engines in section, shown in the side view.
  • This inventive, axially flow-through coolant pump with a pump housing 2, a suction inlet side arranged at this flow inlet opening 3 and a pump housing on the pressure side arranged flow outlet 4, a rotatably mounted in / on the pump housing 2 by means of a pump bearing 5, rotatably connected to a pulley 1 pump shaft 6, a on the drive side next to the flow inlet opening 3 in a seal seat 7 in the pump housing 2 between this and the pump shaft 6 arranged pump shaft seal 8, with a rotatably arranged in the pump housing 2 stator 9 with vanes 10, in which a bearing holder 11 is located, in which a sliding bearing 12 is arranged , in which the pump shaft 6 is mounted with its the drive side, for example, the pulley 1, opposite pump shaft end, wherein rotatably on the pump
  • Halbaxialschaufelrad, Francis and diagonal vane wheels are characterized by a three-dimensional spatially curved blade geometry. Under optimal boundary conditions and with minimum gap dimension, such hemi-axial and Francis and diagonal vane wheels can achieve an efficiency of up to 80%, even with speeds that are normal for coolant pumps, due to their spatially curved blades and the radial flow outlet. Compared to the Axialschaufelrastn used in the prior art in axially flowed coolant pump, Halbaxialschaufelrast, Francis and Diagonalschaufelrion cavitation insensitive and allow for limited space a significant increase in pressure.
  • the pump shaft 6 mounted on both sides on the one hand in the pump bearing 5 and the other hand in a sliding bearing 12 in the stator 9 ensures a minimum annular gap 13 between the impeller 14 and the stator 9, wherein the impeller (14) from the stator (9) a minimum annular gap (13) is spaced so that the impeller (14) both the front side of the adjacent outer edge of the guide cone (16), as well as the front side of the adjacent outer edge of the Leithutes (17) is minimally spaced around the annular gap (13), so in that the stator inlet edges running parallel to the impeller outlet edges form two spaced-apart sealing gap geometries, whereby a flow-technically optimal transition of the volumetric flow volume flowing diagonally out of the impeller 14 directly into the stator 9 according to the invention is ensured.
  • the diagonally outward from the impeller 14 exiting flow rate is, characterized in that the impeller 14 is both frontally spaced from the adjacent outer edge of the guide cone 16, as well as the front side of the adjacent outer edge of the Leithutes 17 by a respective minimum annular gap 13 (a "sealing gap"), optimally introduced into the with a minimum annular gap 13 adjacent, inventively constructed stator 9, and immediately after the bounded by the two sealing gap geometries transition region, according to the invention in the stator 9 immediately "deflected".
  • a respective minimum annular gap 13 a "sealing gap”
  • the stator 9 is characterized in that it has an inner, conically tapering in the flow direction cone 16, and spaced therefrom arranged an outer conical Leithut 17, and the traffic cone 16 with the Leithut 17 via three-dimensional, spatially curved vanes 10 is.
  • the coolant pump according to the invention also ensures high reliability and reliability with a very long service life due to its robust fluidic design even when loaded with dirty cargo coolant.
  • cavitation-insensitive pump ensures in its entirety with a minimum volume of construction high efficiency, and allows despite a very limited space a significant increase in pressure and is characterized at the same time by a very compact, manufacturing and assembly technology simple, inexpensive and robust design.
  • the coolant pump according to the invention over the known in the art axially flowed through coolant pumps, due to the arrangement and the interaction of the modules of the invention, surprisingly also characterized in particular by a stable course of the characteristic of the volume flow through the pump pressure at a constant speed.
  • the coolant pump according to the invention allows a very significant increase in the pump pressure compared to the axial coolant pump of the prior art with the same space / installation volume and the same speed.
  • the design shown has an inflow chamber 19, the chamber length L is about 0.9 times the inner diameter D.
  • This inflow chamber 19 according to the invention causes an undisturbed inflow, in particular serves to "even out” the intake volumetric flow and thereby significantly contributes to a further optimization of the effects according to the invention.
  • a guide tongue 18 is arranged on the free flow end of the guide cap 17. According to the invention, this guide tongue 18 avoids eddies in the region of the pressure-side flow outlet and also serves to further optimize the effects according to the invention.
  • the solution according to the invention in its entirety but also that the inventive solution, compared to the axially flowed coolant pumps of the prior art, with completely closed / istschieberten main flow channel 21 requires a much lower drive power of the pump shaft 6, so that the efficiency of the invention, axially flowed through coolant pump is thereby increased again. In this in the FIG.
  • a coolant outlet flange 20 with the main flow channel 21 is arranged in the region of the flow outlet opening 4 on the pump housing 2 of the coolant pump of the invention flowing through axially.
  • This main flow channel 21 opens, as usual in the art, in the coolant circuit and allows, for example in conjunction with actuators, the optimal cooling of the cylinder crankcase, the cylinder head, as well as the cooling of special components, such as exhaust gas recirculation, the exhaust manifold, but also the heat supply of the heating of the passenger compartment, etc.

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

Claims (5)

  1. Pompe de refroidissement construite selon le principe d'une pompe de refroidissement à entraînement mécanique pour moteurs à combustion avec un carter de pompe (2) avec une ouverture d'admission de courant (3) et une ouverture de sortie de courant (4), un arbre de pompe (6) disposé dans/sur le carter de pompe (2) de manière rotative au moyen d'un palier de pompe (5), un joint d'arbre de pompe (8) disposé du côté de l'entraînement à côté de l'ouverture d'admission de courant (3) dans une garniture (7), dans le carter de pompe (2) entre celui-ci et l'arbre de pompe (6), avec une roue directrice (9) équipée de pales directrice (10) fixe quant à la rotation et disposée dans le carter de pompe (2), dans laquelle roue directrice (9) se trouve un logement de palier (11) dans lequel est disposé un palier glissant (12), dans lequel est disposé l'arbre de pompe (6) avec son extrémité d'arbre de pompe située à l'opposé du côté d'entraînement, une roue (14) avec pales (15) étant disposée de manière fixe quant à la rotation sur l'arbre de pompe (6), au voisinage de la roue directrice (9) avec le palier glissant (12) en direction de l'ouverture d'admission de courant (3) autour d'une fente annulaire (13), et que l'ouverture d'admission de courant (3) est disposée latéralement par rapport à l'axe central d'arbre de pompe (6), de telle manière que l'admission de courant s'effectue en biais par rapport à l'axe de rotation de la roue (14), caractérisée par le fait
    - que la roue (14) est une roue à ailettes semi-axiale avec des pales (15) courbées de manière tridimensionnelle, et
    - que la roue directrice (9) fixe quant à la rotation dans le carter de pompe (2) possède un cône directeur (16) interne effilé en direction du courant et un chapeau directeur (17) externe de forme conique à une certaine distance du cône directeur (16), et
    - que le cône directeur (16) et le chapeau directeur (17), espacés l'un de l'autre de manière symétrique, sont reliés au moyen de pales directrices (10) courbées de manière tridimensionnelle, et
    - que la roue (14) est espacée de la roue directrice (9) par une fente annulaire (13) minimale en forme de fente d'étanchéité, la roue (14) étant espacée de manière minimale sur le côté frontal du bord extérieur voisin du cône directeur (16) comme également du bord extérieur voisin du chapeau directeur (17) par une fente annulaire (13) en forme de fente d'étanchéité, et
    - qu'une chambre d'amission (19) d'un diamètre intérieur (D) est disposée dans le carter de pompe (2) de manière symétrique en rotation par rapport à l'arbre de pompe (6) et placée immédiatement devant la roue (14), la longueur de chambre (L) se trouvant dans un intervalle de 0,7 à 1,5 fois le diamètre intérieur (D).
  2. Pompe de refroidissement selon l'exigence 1 caractérisée par le fait qu'une languette directrice (18) est disposée sur l'extrémité libre du chapeau directeur (17).
  3. Pompe de refroidissement selon l'exigence 1 ou l'exigence 2 caractérisée par le fait que, dans la zone d'ouverture de sortie de courant (4) sur le carter de pompe (2), une bride de sortie de liquide de refroidissement (20) est disposée.
  4. Pompe de refroidissement selon une ou plusieurs des exigences 1 à 3 caractérisée par le fait que la pompe de refroidissement entraînée mécaniquement est mise en rotation par une poulie à courroie (1), une roue dentée ou un arbre d'emboîtement.
  5. Pompe de refroidissement selon une ou plusieurs des exigences 1 à 4 caractérisée par le fait que la roue (14) est une roue de type Francis ou une roue à ailettes diagonale avec des pales (15) courbées de manière tridimensionnelle.
EP11811520.3A 2010-12-04 2011-12-01 Pompe de refroidissement Active EP2646693B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010053510.9A DE102010053510B4 (de) 2010-12-04 2010-12-04 Kühlmittelpumpe
PCT/DE2011/002061 WO2012072068A1 (fr) 2010-12-04 2011-12-01 Pompe de refroidissement

Publications (2)

Publication Number Publication Date
EP2646693A1 EP2646693A1 (fr) 2013-10-09
EP2646693B1 true EP2646693B1 (fr) 2016-01-13

Family

ID=45528860

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11811520.3A Active EP2646693B1 (fr) 2010-12-04 2011-12-01 Pompe de refroidissement

Country Status (7)

Country Link
US (1) US20130272848A1 (fr)
EP (1) EP2646693B1 (fr)
JP (1) JP5917549B2 (fr)
CN (1) CN103299081B (fr)
BR (1) BR112013013637B1 (fr)
DE (1) DE102010053510B4 (fr)
WO (1) WO2012072068A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10400659B2 (en) * 2014-07-21 2019-09-03 Nidec Gpm Gmbh Coolant pump with integrated closed-loop control
DE102014019609B4 (de) 2014-12-30 2019-08-22 Nidec Gpm Gmbh Kühlmittelpumpe
DE102016219273A1 (de) * 2016-10-05 2018-04-05 Bayerische Motoren Werke Aktiengesellschaft Elektrische Pumpe für ein Fahrzeug, insbesondere für ein Kraftfahrzeug, sowie Fahrzeug
CN107091238A (zh) * 2017-06-16 2017-08-25 北京富特盘式电机有限公司 变压器轴流泵
DE102017120191B3 (de) 2017-09-01 2018-12-06 Nidec Gpm Gmbh Regelbare Kühlmittelpumpe für Haupt- und Nebenförderkreislauf
DE102020003431A1 (de) 2020-06-08 2021-12-09 Daimler Ag Kühlmittelpumpe für ein Kraftfahrzeug, insbesondere für einen Kraftwagen

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Also Published As

Publication number Publication date
JP5917549B2 (ja) 2016-05-18
CN103299081A (zh) 2013-09-11
EP2646693A1 (fr) 2013-10-09
WO2012072068A4 (fr) 2012-08-09
BR112013013637B1 (pt) 2020-12-29
WO2012072068A1 (fr) 2012-06-07
WO2012072068A9 (fr) 2012-12-13
DE102010053510B4 (de) 2014-01-23
JP2013545021A (ja) 2013-12-19
DE102010053510A1 (de) 2012-06-06
CN103299081B (zh) 2016-04-27
BR112013013637A2 (pt) 2019-12-31
US20130272848A1 (en) 2013-10-17

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