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EP0348674B1 - Einrichtung zur Kennfelderweiterung eines Radialverdichters - Google Patents

Einrichtung zur Kennfelderweiterung eines Radialverdichters Download PDF

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Publication number
EP0348674B1
EP0348674B1 EP89109560A EP89109560A EP0348674B1 EP 0348674 B1 EP0348674 B1 EP 0348674B1 EP 89109560 A EP89109560 A EP 89109560A EP 89109560 A EP89109560 A EP 89109560A EP 0348674 B1 EP0348674 B1 EP 0348674B1
Authority
EP
European Patent Office
Prior art keywords
impeller
outside diameter
ratio
recess
inlet
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.)
Expired - Lifetime
Application number
EP89109560A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0348674A1 (de
Inventor
Karl-Heinz Dr. Rohne
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.)
ABB Asea Brown Boveri Ltd
Original Assignee
ABB Asea Brown Boveri Ltd
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 ABB Asea Brown Boveri Ltd filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0348674A1 publication Critical patent/EP0348674A1/de
Application granted granted Critical
Publication of EP0348674B1 publication Critical patent/EP0348674B1/de
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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/914—Device to control boundary layer

Definitions

  • the present invention relates to a device for expanding the characteristic map of a radial compressor.
  • turbocompressors be they radial or axial
  • the aim is to achieve stable characteristics that drop monotonically with increasing flow without hysteresis.
  • stable characteristics are more difficult to achieve the greater the pressure ratio at the design point.
  • practice tries to help itself to achieve the desired characteristics by means of additional stabilization devices. Due to differences in the design of the blades and in the structures of the tear-off areas during part-load operation, no clear technical solution has emerged to date, according to which a general non-slip stabilizing device could be derived.
  • a stabilizing device has become known in a radial compressor, which is characterized in that the inner housing has radial or quasi-radial bores as the sheathing of the impeller. These holes create a connection between the inflow channel and the blades, whereby they are more or less covered by the blades on the blade side. With such bores, the pumping and stability limits are shifted in the form of a map line, but this involves the loss of high efficiency, which can amount to 4 - 5 percentage points.
  • the proposed solution cannot substantially achieve the desired map expansion at low throughputs that would be necessary due to the instabilities that occur with a specific type of operation. What is also important is the fact that this minimal stabilizing effect has to be bought through a disproportionately large loss in efficiency.
  • the invention seeks to remedy this.
  • the object of the invention is to provide, in the case of radial compressors, a device for expanding the characteristic map to small throughputs by stabilizing the impeller flow in the inlet area with predeterminable accuracy.
  • the main advantage of the invention is that this device behaves neutrally as long as the radial compressor delivers the full volume flow; only when different flow structures occur, in particular at partial load, the device comes into operation and prevents the phenomenon of separation from appearing over the entire partial load range. This prevents the dreaded "pumping", which results in stable characteristics.
  • Another advantage of the invention can be seen in the fact that the device represents a simple structural arrangement that can be provided in any radial compressor, regardless of its technical specification.
  • Fig. 1 shows a partial view of a radial compressor in the area of an intended device for expanding the map when operating such a compressor.
  • the device generally effects a stabilization of the impeller flow in the inlet area during part-load operation.
  • the radial compressor consists of housing 1 and impeller 2, the above-mentioned stabilization device being provided in front of impeller 2, which in turn consists of a stabilizer opening 5, a stabilization ring 3 and a number of stabilizer blades 4.
  • the stabilizer opening 5 has the shape of an inner groove and extends in the radial direction, starting from the surface of the inlet channel 6, into the housing 1 by a certain depth; in the axial direction it extends approximately upstream by a certain length from the inflow edge of the impeller 2.
  • the stabilization ring 3 is integrated in the stabilizer opening 5, its inner circumferential surface extending into the continuation of the surface of the inlet channel 6.
  • the outer circumference of the stabilizing ring 3 is equipped with a number of blades which, in radial expansion, fill the remaining clear width of the stabilizer opening 5 and are anchored there.
  • the wall thickness of the stabilization ring 3 represents a function of the operationally required strength and stability. For fluidic considerations, the wall thickness of the stabilization ring 3 must not unnecessarily come at the expense of the height of the stabilizer blades 4. Accordingly, one is dealing with a bladed stabilizer variant, which guarantees a better effect towards eliminating a hysteresis or instability area compared to a bladed version.
  • the correct design of the stabilizer consists first of all in the correct choice of the outside diameter of the stabilizing ring 3, which is to be matched to the compressor, that is to say to the outside diameter at the impeller inlet, so that on the one hand only a little flows through the stabilizer opening 5 at the best point, so that the efficiency does not fall, on the other hand, the largest possible flow 8 must circulate at partial load.
  • the outside diameter of the stabilizing ring 3 which is to be matched to the compressor, that is to say to the outside diameter at the impeller inlet, so that on the one hand only a little flows through the stabilizer opening 5 at the best point, so that the efficiency does not fall, on the other hand, the largest possible flow 8 must circulate at partial load.
  • the partial flow 9 also receives a counter-swirl, whereby the efficiency tends to grow.
  • the exemplary embodiment mentioned here is designed such that the impeller 2 projects into the stabilizer opening 5. This has the following relevance: The further the impeller 2 protrudes into the stabilizer opening 5, the more work is transferred to the circulating air, the greater the circulating volume flow 8 and the greater the stabilizing effect of the device.
  • the width of the stabilizer blade 4 in the flow direction of the recirculating part-load flow 8 is variable, as the dashed-line stabilizer blade 4a wants to show, and can occupy the entire remaining width of the stabilizer opening 5 in this plane of expansion.
  • the widest possible stabilizer blade 4a has a channeling effect on the partial flows 8, 9 and helps to increase the stability of the device in the event of partial and overload.
  • FIG. 2 also shows a radial compressor according to FIG. 1 with a development of the stabilization ring 3 and stabilizer blade 4a for the purpose of achieving a flow improvement in the stabilizer opening 5 under partial load.
  • the stabilization ring 3a is profiled, while the stabilizer blade 4a, which has maximum axial expansion in the flow direction of the partial load flow 8, is further developed by an inflow aid 4b.
  • FIG. 2 further shows an example of the increase in the stabilizing effect of the device postulated under FIG. 1 by extending the impeller 2a in the countercurrent direction to far into the stabilizer opening 5. As can be seen in FIG. 2, it is structurally feasible to have the impeller 2a protrude into the stabilizer opening 5 as far as the stabilizing ring 3a.
  • the correct design of the stabilizer consists first of all in the correct choice of the outer diameter d of the stabilizing ring 3. It is obvious that this diameter d must be in a certain ratio to the outer diameter of the impeller inlet opening Y. to ensure the envisaged advantages of operating a radial compressor with a device for stabilizing the impeller flow in the inlet area, in particular under partial load.
  • a correct choice of the outer diameter of the stabilizing ring d is to limit it in the interval 1.02 - 1.05 to the outer diameter of the impeller inlet opening Y.
  • the sizes of the other elements of the device are derived from this choice of output, the dimensions of these elements being subsequently expressed for the sake of clarity as a ratio to the respective outer diameter of the impeller inlet opening Y.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP89109560A 1988-06-29 1989-05-26 Einrichtung zur Kennfelderweiterung eines Radialverdichters Expired - Lifetime EP0348674B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH2478/88A CH675279A5 (ko) 1988-06-29 1988-06-29
CH2478/88 1988-06-29
IN485MA1989 IN172509B (ko) 1988-06-29 1989-06-20

Publications (2)

Publication Number Publication Date
EP0348674A1 EP0348674A1 (de) 1990-01-03
EP0348674B1 true EP0348674B1 (de) 1992-12-16

Family

ID=25690563

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89109560A Expired - Lifetime EP0348674B1 (de) 1988-06-29 1989-05-26 Einrichtung zur Kennfelderweiterung eines Radialverdichters

Country Status (5)

Country Link
US (1) US4990053A (ko)
EP (1) EP0348674B1 (ko)
CH (1) CH675279A5 (ko)
IN (1) IN172509B (ko)
RU (1) RU1831590C (ko)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102927053A (zh) * 2012-11-12 2013-02-13 西安交通大学 周向槽机匣处理方法
DE102015111462B3 (de) * 2015-07-15 2016-09-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verdichter mit Rückströmkanal und verstellbaren Vorleitschaufeln

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CN102927053A (zh) * 2012-11-12 2013-02-13 西安交通大学 周向槽机匣处理方法
DE102015111462B3 (de) * 2015-07-15 2016-09-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verdichter mit Rückströmkanal und verstellbaren Vorleitschaufeln

Also Published As

Publication number Publication date
IN172509B (ko) 1993-09-04
JPH0242199A (ja) 1990-02-13
EP0348674A1 (de) 1990-01-03
US4990053A (en) 1991-02-05
RU1831590C (ru) 1993-07-30
CH675279A5 (ko) 1990-09-14

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