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WO2012167961A1 - Pompe à liquide de refroidissement réglable en continu - Google Patents

Pompe à liquide de refroidissement réglable en continu Download PDF

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Publication number
WO2012167961A1
WO2012167961A1 PCT/EP2012/054515 EP2012054515W WO2012167961A1 WO 2012167961 A1 WO2012167961 A1 WO 2012167961A1 EP 2012054515 W EP2012054515 W EP 2012054515W WO 2012167961 A1 WO2012167961 A1 WO 2012167961A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
coolant pump
closure
guide
pump according
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.)
Ceased
Application number
PCT/EP2012/054515
Other languages
German (de)
English (en)
Inventor
Sebastian Hurst
Markus Popp
Carsten LÜKEN
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to US14/004,803 priority Critical patent/US20140003913A1/en
Priority to CN201280026098.7A priority patent/CN103597212B/zh
Publication of WO2012167961A1 publication Critical patent/WO2012167961A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps

Definitions

  • the present invention relates to a coolant pump, for a cooling circuit of an internal combustion engine, with a pump housing.
  • a drivable shaft is mounted, at one end of an impeller is mounted, which has in a suction chamber protruding wings and is connected to a cover plate. Due to the rotation of the cover plate and the impeller having impeller fluid is sucked through a suction nozzle of the pump housing in the suction chamber and transported via the wings further into the pump housing.
  • a guide disc which can be displaced axially via an actuating unit is arranged.
  • the guide disk has a contour corresponding to the impeller and a projection oriented in the direction of the impeller.
  • the coolant pump In order to achieve rapid heating of the internal combustion engine and to adjust the engine temperature, the coolant pump should be switchable and, at best, controllable. This is achieved in a targeted manner by adjusting the delivery flow.
  • the guide disk In order to adjust the delivery or the volume flow, the guide disk is displaced axially in the pump within the impeller. This must be done via an actuator, which is as compact as possible, preferably in the axial direction, installed.
  • a coolant pump according to the aforementioned type is known from the document DE 10 2008 046 424 A1.
  • the object of the invention is to provide a switchable or controllable coolant pump whose actuator does not require any additional costs or installation space in order to apply the forces for adjusting the guide disk.
  • the guide disk has at least one opening.
  • the existing opening reduces the effective pressure difference between the front face plate and the rear face plate, which in turn reduces the axial force needed to move the face plate.
  • the flow exchange between Leitusionnvorder- and Leitusionn Wegseite is facilitated.
  • the fluid conveyed radially behind the guide disk has a centrifugal pressure which is typical of the wing impeller. Together with a certain amount of accumulation, which arises after entering through the holes in the axial impingement on the impeller rear wall, a mean pressure is generated behind the guide disk.
  • the fluid under pressure thus has a force component which leads in the direction of "closing the guide disk.”
  • the direction “closing the guide disk” describes the axial displacement of the guide disk in the direction of the cover disk. This results in a reduction of the resulting force in the direction of "opening the guide disc.”
  • the direction “opening the guide disc” describes the axial displacement of the guide disc in the direction of the impeller.
  • the actuator is relieved in terms of the force applied in its traversing function. It has proved to be advantageous to introduce more than one opening in the guide disk.
  • the openings may have different shapes, for example flow-optimized shapes for utilizing flow effects, as well as radial or circumferentially extending openings running on the guide disk or production-optimized molds for more favorable production.
  • the most effective arrangement of the openings is in the region near the disc rotation axis.
  • the diagram representation in FIG. 4 shows how the fluid forces behave in dependence on the degree of opening of the guide disk. Ideally, the fluid force is zero, thereby the actuator could move the guide disc axially without additional effort. In the case of a guide disk without openings, the achievement of a fluid force of zero, as can be seen from the diagram, is not possible. The higher the number of openings, the faster the force level drops.
  • the diagram also shows that the force level assumes a negative sign above a certain opening degree of the guide disk and a certain number of openings.
  • a negative force level or negative fluid forces mean that the guide disk moves in the direction of the cover disk and thus prevents the fluid flow within the water pump. This should be avoided. So that the actuator can apply sufficient force against the negative fluid forces, it would have to be dimensioned larger or larger, which in turn would cause additional costs.
  • the actuator may optionally have a spring.
  • the spring causes the guide plate to be indirectly pressurized via the shaft in the direction of "open the guide disk.”
  • This embodiment represents a fail-safe solution. If the actuator fails and the guide plate closes in the direction of the guide disk due to a negative fluid force is pulled, resulting in a reduction of the coolant flow, the spring generates a back pressure to prevent the guide disc from closing. In this embodiment, however, one would have the entire forces curves around the Increase the preload of the spring. As a result, the previously obtained loss of energy would be partially canceled.
  • closure contour has more than one closure element.
  • the individual closure elements may differ in their dimensions (length, curvature, pitch, diameter).
  • the closure elements may be tapered, i. the closure elements taper from the impeller towards the cover disc.
  • closure elements are designed wing-like.
  • the actuating unit comprises an actuator which actuates independently of the rotational speed of the impeller.
  • FIG. 1 shows a coolant pump for a cooling circuit of an internal combustion engine with a pump housing 1.
  • a drivable shaft 2a is mounted, at one end of an impeller 4 is attached.
  • the impeller 4 has in the suction chamber 7 protruding wings 6.
  • the impeller 4 and the cover plate 9 are connected together.
  • fluid is conveyed via a suction nozzle 10 of the pump housing 1 into the suction chamber 7.
  • an actuator 3 axially displaceable guide disc 12 is arranged.
  • the guide disk 12 has a contour corresponding to the impeller 4 and a projection 13 oriented in the direction of the impeller 4.
  • the coolant pump In order to achieve rapid heating of the internal combustion engine and to set the engine temperature specifically, the coolant pump must be controllable or switchable. For this purpose, a volume flow is adjusted as needed.
  • the guide disk 12 In order to adjust the volume flow, the guide disk 12 is displaced axially in the pump housing 1.
  • the guide disc 12 displaced within the impeller 4 and the cover disk 9 changes the degree of opening and thus controls the passage of the volume flow.
  • the adjusting unit 3 comprises both the shaft 2a and an axially displaceable in the shaft 2a push rod 2b, and a push rod 2b aktuie- rende actuator 14.
  • the push rod 2b is in direct communication with the guide plate 12.
  • the displacement of the guide plate 12 is through the Actuator 14 controlled.
  • the actuator 14 should be integrated into the coolant pump in as little space as possible. For this reason, it is necessary to keep the forces resulting from the volume flow on the guide disk 12 as low as possible in order to be able to select the actuator 14 in a space-saving manner.
  • the force level can be reduced to the guide plate 12 and thus to the actuator 14, openings 1 1 are introduced into the guide plate 12 according to the invention.
  • the effective pressure difference between Leitusionnvorderseite (surface facing the cover plate) and Leitusionngurseite (surface which faces the impeller) is reduced. This in turn results in a reduction of the fluid forces of the volume flow acting on the guide disk 12. The flow exchange between Leitusionnvorder- and Leitusionn Wegseite is thus facilitated.
  • the radially conveyed fluid generates a pressure pad on the back of the disc.
  • This pressure results in a force component in the direction of "closing the guide plate", which in turn causes the resulting force in the direction “Leitbin open” reduces and thereby relieves the actuator 14 in its Verfahrfunktion.
  • the Leitusion 12 is closed when the Leitusionnvorderseite abuts against the cover plate 9 and no flow can flow more
  • the opening degree of the guide plate 12 is an indication of the amount of the coolant pump 4 shows the relationship between the number of openings 1 1 introduced into the guide disk 12, the degree of opening of the guide disk 12 and the fluid forces acting on the guide disk 1 2.
  • This idealized forces curve 20 can be implemented only if S x is "bound" to one of the nearest operating points after reaching the respective selected operating point. This is achieved by varying the number of openings 1 1 of the guide pulley 12, and the opening degree of the guide pulley 12 reached.
  • FIGS. 2b and 2d show the guide disk 12 in an open position with closed openings 11. This corresponds in the diagram to a working range of 1 00% opening degree up to operating point S1.
  • FIGS. 2a and 2c show the guide disk 1 2 in the closed state with the openings 11 closed. This corresponds in the diagram, depending on the degree of opening, to the working range between the operating points S3 to S4 or 0% opening degree.

Landscapes

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

Abstract

L'invention concerne une pompe à liquide de refroidissement pour un circuit liquide de refroidissement d'un moteur à combustion interne, comprenant un corps de pompe (1), dans lequel est logé un arbre (2a) pouvant être entraîné, à l'extrémité duquel est fixée une roue à aubes (4), qui présente des aubes (6) pénétrant dans une chambre d'aspiration (7) et qui est reliée à un disque de recouvrement (9), un fluide étant aspiré par la rotation de la roue à aubes (4), conjointement avec le disque de recouvrement (9), par une tubulure d'aspiration (10) du corps de pompe (1) dans la chambre d'aspiration (7) et transporté, par des aubes (6), dans le corps de pompe (1), un disque de guidage (12), présentant un contour correspondant à la roue à aubes (4) et un porte-à-faux (13) orienté vers la roue à aubes (4), coulissant axialement par une unité de réglage (3), étant disposé entre la roue à aubes (4) et le disque de recouvrement (9), caractérisée en ce que le disque de guidage (12) présente au moins une ouverture (11), la roue de guidage (4) présente un contour de fermeture (5), qui pointe vers la roue de guidage (12) et le contour de fermeture (5) pouvant s'insérer dans une des ouvertures (11) du disque de guidage (12) et la fermant partiellement ou totalement.
PCT/EP2012/054515 2011-06-07 2012-03-15 Pompe à liquide de refroidissement réglable en continu Ceased WO2012167961A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US14/004,803 US20140003913A1 (en) 2011-06-07 2012-03-15 Infinitely adjustable coolant pump
CN201280026098.7A CN103597212B (zh) 2011-06-07 2012-03-15 可无级调节的冷却介质泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011077029A DE102011077029A1 (de) 2011-06-07 2011-06-07 Stufenlos regelbare Kühlmittelpumpe
DE102011077029.1 2011-06-07

Publications (1)

Publication Number Publication Date
WO2012167961A1 true WO2012167961A1 (fr) 2012-12-13

Family

ID=45875946

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/054515 Ceased WO2012167961A1 (fr) 2011-06-07 2012-03-15 Pompe à liquide de refroidissement réglable en continu

Country Status (4)

Country Link
US (1) US20140003913A1 (fr)
CN (1) CN103597212B (fr)
DE (1) DE102011077029A1 (fr)
WO (1) WO2012167961A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011077030A1 (de) * 2011-06-07 2012-12-13 Schaeffler Technologies AG & Co. KG Regelbare Kühlmittelpumpe
CN103629121A (zh) * 2013-12-12 2014-03-12 兰州理工大学 一种离心泵叶轮动态轴向力的测试装置
US12171083B2 (en) * 2021-08-22 2024-12-17 Cooler Master Co., Ltd. Variable-part liquid cooling pumping unit
SE2330616A1 (en) * 2023-12-28 2025-06-29 Swegon Operations Ab A centrifugal fan arrangement, a control system for a centrifugal fan arrangement and a method for controlling a centrifugal fan arrangement

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2255503A1 (de) * 1972-11-13 1974-05-16 Heinz Knebel Einrichtung zur stufenlos regulierbaren ausstossmengen-regelung fuer kreiselpumpen, ventilatoren und geblaese
DE3732038A1 (de) * 1986-09-30 1988-04-07 Mitsubishi Motors Corp Pumpe
US4828455A (en) * 1982-12-21 1989-05-09 Aisin Seiki Kabushiki Kaisha Temperature responsive blade shroud-disk for thermostatic water pump
DE9200240U1 (de) * 1992-01-11 1992-02-27 Kultscher, Armin Henry, 3300 Braunschweig Variable Strömungsmaschine
US5169286A (en) * 1989-03-09 1992-12-08 Yutaka Yamada Variable capacity centrifugal water pump with movable pressure chamber formed by impeller
US6074167A (en) * 1999-02-05 2000-06-13 Woodward Governor Company Variable geometry centrifugal pump
DE19901123A1 (de) * 1999-01-14 2000-07-20 Bosch Gmbh Robert Regelbare Radialpumpe, insbesondere zum Fördern eines Kühlmittels für ein Kraftfahrzeug
DE102008046424A1 (de) 2008-09-09 2010-03-11 Schaeffler Kg Regelbare Kühlmittelpumpe

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5800120A (en) * 1995-11-07 1998-09-01 A. W. Chesterton Co. Pump impeller with adjustable blades
US20070022979A1 (en) * 2005-08-01 2007-02-01 The Timken Company Coolant pump for internal combustion engine
GB0517583D0 (en) * 2005-08-30 2005-10-05 Flowork Systems Ii Llc Sealing system for coolant pump having movable vanes
DE102011077030A1 (de) * 2011-06-07 2012-12-13 Schaeffler Technologies AG & Co. KG Regelbare Kühlmittelpumpe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2255503A1 (de) * 1972-11-13 1974-05-16 Heinz Knebel Einrichtung zur stufenlos regulierbaren ausstossmengen-regelung fuer kreiselpumpen, ventilatoren und geblaese
US4828455A (en) * 1982-12-21 1989-05-09 Aisin Seiki Kabushiki Kaisha Temperature responsive blade shroud-disk for thermostatic water pump
DE3732038A1 (de) * 1986-09-30 1988-04-07 Mitsubishi Motors Corp Pumpe
US5169286A (en) * 1989-03-09 1992-12-08 Yutaka Yamada Variable capacity centrifugal water pump with movable pressure chamber formed by impeller
DE9200240U1 (de) * 1992-01-11 1992-02-27 Kultscher, Armin Henry, 3300 Braunschweig Variable Strömungsmaschine
DE19901123A1 (de) * 1999-01-14 2000-07-20 Bosch Gmbh Robert Regelbare Radialpumpe, insbesondere zum Fördern eines Kühlmittels für ein Kraftfahrzeug
US6074167A (en) * 1999-02-05 2000-06-13 Woodward Governor Company Variable geometry centrifugal pump
DE102008046424A1 (de) 2008-09-09 2010-03-11 Schaeffler Kg Regelbare Kühlmittelpumpe

Also Published As

Publication number Publication date
DE102011077029A1 (de) 2012-12-13
CN103597212B (zh) 2016-03-30
US20140003913A1 (en) 2014-01-02
CN103597212A (zh) 2014-02-19

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