EP1538338A1 - Pompe radiale - Google Patents

Pompe radiale Download PDF

Info

Publication number
EP1538338A1
EP1538338A1 EP03450273A EP03450273A EP1538338A1 EP 1538338 A1 EP1538338 A1 EP 1538338A1 EP 03450273 A EP03450273 A EP 03450273A EP 03450273 A EP03450273 A EP 03450273A EP 1538338 A1 EP1538338 A1 EP 1538338A1
Authority
EP
European Patent Office
Prior art keywords
cover ring
impeller
housing
radial pump
guide surface
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.)
Granted
Application number
EP03450273A
Other languages
German (de)
English (en)
Other versions
EP1538338B1 (fr
Inventor
Alfred Ing. Götschhofer
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.)
TCG Unitech Systemtechnik GmbH
Original Assignee
TCG Unitech Systemtechnik 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 TCG Unitech Systemtechnik GmbH filed Critical TCG Unitech Systemtechnik GmbH
Priority to EP03450273A priority Critical patent/EP1538338B1/fr
Priority to AT03450273T priority patent/ATE330127T1/de
Priority to DE50303864T priority patent/DE50303864D1/de
Priority to AT04450193T priority patent/ATE346240T1/de
Priority to EP20040450193 priority patent/EP1538339B1/fr
Priority to DE502004002076T priority patent/DE502004002076D1/de
Publication of EP1538338A1 publication Critical patent/EP1538338A1/fr
Application granted granted Critical
Publication of EP1538338B1 publication Critical patent/EP1538338B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D15/0033—By-passing by increasing clearance between impeller and its casing

Definitions

  • the invention relates to a radial pump with a housing in which a is rotatably supported by a shaft driven impeller, with a on the Suction side of the impeller in the housing axially in the direction of the impeller axis between two end positions slidably mounted cover ring, wherein by moving the Cover ring from a limited by a housing stop first end position a gap formed between the impeller and the housing can be released.
  • From DE 41 42 120 A1 is a cooling water pump for an internal combustion engine known.
  • a displaceable in the axial direction Inserted cover ring In one between a water-carrying channel and a water pump housing arranged opening is a displaceable in the axial direction Inserted cover ring.
  • the cover ring is controlled by an actuator depending on Parameters of the internal combustion engine adjustable.
  • By shifting the Deckringes is the width of a gap between the ring and the impeller of Variable water pump, so that the cooling water flow rate is changeable. This makes it possible to shorten the warm-up phase of the internal combustion engine and the Reduce amount of harmful exhaust gas components.
  • the disadvantage is that for Change in the position of the bezel a significant control technology Effort is required.
  • cooling water pumps of internal combustion engines are designed that even at relatively low engine speeds high coolant flows can be provided.
  • the subsidized Volume flow but also the power consumption of the pump much higher than required, which has a negative effect on fuel consumption. apart Of these, cavitation phenomena may occur in the high speed range.
  • the object of the invention is the simplest possible way the flow rate and to reduce the power consumption at high speeds.
  • this is achieved in that the cover ring automatically in dependence the pressure difference between the pressure and suction side of the impeller adjustable is.
  • the gap between impeller and housing is independent adapted to the current impeller speed, thereby consuming actuators can be omitted.
  • an at least formed by a return element restoring force in the direction of the first End position acts on the cover ring.
  • the return element by a resilient biasing means, preferably a return spring, is formed, which acts in the direction of the impeller axis on the cover ring.
  • the cover ring in at least one defined position, preferably at least in the first end position, by a positioning element preferably formed by a latching device is positionable.
  • a positioning element preferably formed by a latching device
  • the positioning element a about spring-loaded radially with respect to the wheel axis, preferably by a Ball formed pressure body, which along a guide surface is slidably disposed and which in the defined position with a reciprocal shaped latching element cooperates.
  • the locking element can, for example to be a bulge in the guide surface.
  • the Guide surface is formed by a suction-side inner surface of the housing and the pressure body is arranged in the jacket region of the cover ring, wherein preferably a pressure spring acting on the pressure body in a radial bore the cover ring is arranged.
  • the guide surface through the cladding region of Deckringes is formed and that the pressure body in the region of a suction chamber side Inner surface of the housing is arranged, preferably one on the Pressure element acting pressure spring disposed in a radial bore of the housing is.
  • the guide surface with respect to the impeller axis by an angle smaller than about 20 °, preferably less than about 10 ° is inclined.
  • the radial pump 1 has a housing 2, in which a shaft 3 for driving an impeller 4 is rotatably supported by a bearing 5.
  • the suction side the radial pump 1 is denoted by reference numeral 6, the pressure side by reference numeral 7th designated.
  • Around the impeller 4 around the housing 2 forms a spiral channel. 8 out.
  • On the suction side 6 of the impeller 4 is in the housing 2, a cover ring 9 in Direction of the impeller axis 10 between a first and a second end position slidably arranged. In the first end position shown in Fig. 1 is a formed between the impeller 4 and housing 2 gap 11 through the cover ring. 9 obscured, so that leakage flows between the pressure side 7 and suction side 6 prevented become.
  • the cover ring 9 is replaced by at least one return element 12 in the first end position moved or held in this.
  • the return element shown in Fig. 2 12 consists of a formed by a spring plate return spring 14, which acts in the axial direction on the cover ring 9.
  • the positioning element shown in Fig. 3 13 is arranged in the jacket region 15 of the cover ring 9 and has a by a compression spring 16 spring-loaded pressure body 17, wherein the compression spring 16 arranged in a radial bore 18 in the jacket region 15 of the cover ring 9 is.
  • the pressure body 17 can be formed for example by a ball his.
  • the pressure body 17 lies on a through a suction-side inner surface 2a of the housing 2 formed guide surface 19 and slides at axial deflection the cover ring along this, wherein the pressure body 17 in the first End position engages in a formed by a recess 20 form element and thus stabilizing the position of the cover ring 9.
  • To the return movement of the To support the cover ring 9 in the direction of the first end position is the guide surface 19 formed with respect to the impeller axis 10 slightly inclined, wherein the angle ⁇ between the guide surface 19 and the impeller axis 10 is smaller than about 10 ° is.
  • the first end position of the cover ring 9 is located at a through the housing 2 stop 21 formed.
  • the cover ring 9 is moved in response to the pressure difference between the pressure p 2 of the pressure side 7 and the pressure p 1 of the suction side 6 from the first end position determining a rest position in the second end position.
  • the cover ring 9 Up to a predefined rotational speed of the impeller 4, which is associated with a certain flow rate, the cover ring 9 is positioned in the first end position shown in Fig. 1 with a very small gap 11 with respect to the impeller 4, so that an optimum efficiency is achieved.
  • This position is defined on the one hand by the stop 21 in the housing, on the other hand by the return element 12 and the positioning element 13.
  • the return element 12 and the positioning element 13 can also be used in combination in order to ensure a demand-oriented control characteristic.
  • the reset and positioning elements 12, 13 are designed so that at a certain pressure difference p 2 - p 1, an axial displacement of the cover ring 9 takes place away from the impeller 4. Depending on the design of the reset and positioning elements 12, 13, this axial adjustment can take place continuously or abruptly above a certain speed.
  • the increasing axial gap 11 between the impeller 4 and cover ring 9 causes a reduction of the flow rate and thereby a reduction of the Power consumption at high speeds. Furthermore, the high speed range prevents cavitation occurring.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
EP03450273A 2003-12-04 2003-12-04 Pompe radiale Expired - Lifetime EP1538338B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP03450273A EP1538338B1 (fr) 2003-12-04 2003-12-04 Pompe radiale
AT03450273T ATE330127T1 (de) 2003-12-04 2003-12-04 Radialpumpe
DE50303864T DE50303864D1 (de) 2003-12-04 2003-12-04 Radialpumpe
AT04450193T ATE346240T1 (de) 2003-12-04 2004-10-14 Radialpumpe
EP20040450193 EP1538339B1 (fr) 2003-12-04 2004-10-14 Pompe radiale
DE502004002076T DE502004002076D1 (de) 2003-12-04 2004-10-14 Radialpumpe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03450273A EP1538338B1 (fr) 2003-12-04 2003-12-04 Pompe radiale

Publications (2)

Publication Number Publication Date
EP1538338A1 true EP1538338A1 (fr) 2005-06-08
EP1538338B1 EP1538338B1 (fr) 2006-06-14

Family

ID=34443181

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03450273A Expired - Lifetime EP1538338B1 (fr) 2003-12-04 2003-12-04 Pompe radiale

Country Status (3)

Country Link
EP (1) EP1538338B1 (fr)
AT (2) ATE330127T1 (fr)
DE (2) DE50303864D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9869326B2 (en) 2012-12-05 2018-01-16 Wilo Se Centrifugal pump in particular for waste water or polluted water

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US3168870A (en) * 1962-12-12 1965-02-09 Ingersoll Rand Co Centrifugal pump with adjustable capacity
DE1528821A1 (de) * 1962-10-15 1969-10-16 Sulzer Ag Verfahren zur Beeinflussung des Anlaufvorganges einer einstufigen,einflutigen Pumpe oder umkehrbaren Pumpenturbine sowie Pumpe oder Pumpenturbine zur Durchfuehrung des Verfahrens
FR2681906A1 (fr) * 1991-09-27 1993-04-02 Renault Vehicules Ind Pompe centrifuge pour circuit de liquide de refroidissement de moteur a combustion.
DE4142120A1 (de) * 1991-12-20 1993-06-24 Porsche Ag Kuehlwasserpumpe fuer eine brennkraftmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
DE1528821A1 (de) * 1962-10-15 1969-10-16 Sulzer Ag Verfahren zur Beeinflussung des Anlaufvorganges einer einstufigen,einflutigen Pumpe oder umkehrbaren Pumpenturbine sowie Pumpe oder Pumpenturbine zur Durchfuehrung des Verfahrens
US3168870A (en) * 1962-12-12 1965-02-09 Ingersoll Rand Co Centrifugal pump with adjustable capacity
FR2681906A1 (fr) * 1991-09-27 1993-04-02 Renault Vehicules Ind Pompe centrifuge pour circuit de liquide de refroidissement de moteur a combustion.
DE4142120A1 (de) * 1991-12-20 1993-06-24 Porsche Ag Kuehlwasserpumpe fuer eine brennkraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9869326B2 (en) 2012-12-05 2018-01-16 Wilo Se Centrifugal pump in particular for waste water or polluted water

Also Published As

Publication number Publication date
ATE330127T1 (de) 2006-07-15
DE502004002076D1 (de) 2007-01-04
ATE346240T1 (de) 2006-12-15
EP1538338B1 (fr) 2006-06-14
DE50303864D1 (de) 2006-07-27

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