EP0644317A1 - Pompe à anneau liquide - Google Patents

Pompe à anneau liquide Download PDF

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Publication number
EP0644317A1
EP0644317A1 EP94106156A EP94106156A EP0644317A1 EP 0644317 A1 EP0644317 A1 EP 0644317A1 EP 94106156 A EP94106156 A EP 94106156A EP 94106156 A EP94106156 A EP 94106156A EP 0644317 A1 EP0644317 A1 EP 0644317A1
Authority
EP
European Patent Office
Prior art keywords
housing
impeller
work space
liquid ring
space housing
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
EP94106156A
Other languages
German (de)
English (en)
Other versions
EP0644317B1 (fr
Inventor
Klaus Dipl.-Ing. Domagalla
Udo Dipl.-Ing. Segebrecht
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.)
Sihi GmbH and Co KG
Original Assignee
Sihi GmbH 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 Sihi GmbH and Co KG filed Critical Sihi GmbH and Co KG
Priority to CA002131081A priority Critical patent/CA2131081C/fr
Priority to AU71625/94A priority patent/AU673761B2/en
Priority to CZ19942184A priority patent/CZ291259B6/cs
Priority to JP21706994A priority patent/JP3538234B2/ja
Priority to US08/304,534 priority patent/US5509789A/en
Priority to MYPI94002450A priority patent/MY111315A/en
Priority to CN94115333A priority patent/CN1035837C/zh
Priority to SK1119-94A priority patent/SK281523B6/sk
Priority to TW083109028A priority patent/TW257826B/zh
Publication of EP0644317A1 publication Critical patent/EP0644317A1/fr
Application granted granted Critical
Publication of EP0644317B1 publication Critical patent/EP0644317B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids

Definitions

  • the invention relates to a liquid ring gas pump according to the preamble of claim 1.
  • the pump comprises a connection housing flanged to the drive motor, which forms the suction and pressure connections, a cup-shaped work space housing which has a flange for connection to a flange of the Has connection housing, and a control disc arranged between these two housings. All parts of the housing are strongly dimensioned castings. This is common in liquid ring gas pumps because the efficiency is largely dependent on the maintenance of little play between the impeller and the work space housing and this play should not be affected by housing deformation. This is also the reason why the cheaper sheet metal construction, which has long been used in other types of pumps, has not yet found its way into liquid ring gas pumps.
  • the invention has for its object to achieve a more economical production of liquid ring gas pumps without loss of quality.
  • the solution according to the invention consists in the features of claim 1 and preferably the subclaims. It consists mainly in the fact that the work area housing is designed as a pot-shaped, deep-drawn, connection-free sheet metal part.
  • the impeller which forms open cells between the vanes towards the control disk, is largely closed on the side facing away from the control disk by an end disk or a radial expansion of the hub; the overflow paths are therefore longer on this side than on the side cooperating with the control disk, so that greater play can be tolerated.
  • an axial thrust acts on the impeller in the direction of the control disc, so that an approximately increased bearing clearance does not increase the critical gap between the impeller and the control disc, but at most the less critical clearance between the end face of the impeller that is remote from the control disc and the bottom of the working area housing.
  • the medium connections are provided in the connection housing, so that the work area housing cannot be warped due to warping during manufacture or due to the introduction of force during use. This also applies to the drain opening and the operating fluid supply.
  • the work space housing has a substantially radial connecting flange for connection to the connection housing, which is formed in one piece with the rest of the work space housing.
  • This poses the problem that, due to the manufacturing process, a rounding arises at the transition from the cylindrical part of the housing to the flange which forms a peripheral gap adjacent to the control disk.
  • efforts are made to allow the smallest possible distance at the apex of the housing, where the outer edges of the impeller come closest to the circumference of the housing, in order to keep the overflow losses that arise from the overflow of liquid from one cell to the next cell of lower pressure .
  • the gap formed in the rounding of the sheet metal housing represents an additional overflow cross section.
  • the invention has recognized that this effort is unnecessary if the size of the gap does not exceed a certain cross-sectional area. More specifically, it is coming mainly on the area of the gap which is closer to the impeller and which has a larger width than the part of the gap which is further out.
  • the cross-sectional area of the gap as such is therefore less meaningful than the size of the incircle that can be inscribed in the gap cross-sectional area, as stated in claims 3 and 4.
  • This incircle diameter should not exceed 1.5 times, preferably 0.85 times the wall thickness of the work area housing. In general, it should not be larger than 3.5%, preferably 2.5% of the impeller diameter in pumps with a conventional impeller diameter (for example 125 to 210 mm diameter, speed 3000 rpm).
  • Dirt particles that get into the liquid ring and have a higher density than the liquid are caught in the liquid ring and circle around its outer circumference. It is known to provide a dirt removal opening in the control disk on the outer circumference of the liquid ring, through which part of the liquid with the particles can leave the liquid ring.
  • the dirt particles preferably collect in the gap between the rounding of the working space housing and the control disk. It is therefore expedient if the dirt discharge opening is arranged at this gap, i.e. at least adjacent to these, but preferably completely or partially radially outside the inner diameter of the cylindrical part of the work space housing.
  • connection housing 3 is connected via the flange 2, which contains the suction and pressure chamber of the pump and the suction and pressure ports leading to the outside.
  • control disk 4 which contains the suction and pressure openings (not shown), and then the work space housing 5 with the connecting flange 6 and the housing wall 7 remote from the drive.
  • the connecting flange 6 is connected to the connection housing 3 by means of the screws 17 and the control disk 4.
  • the control disk 4 is fastened to the connection housing 3 by means of additional screws 8.
  • the centering of the flange 6, like the centering of the control disk 4 with respect to the connection housing 3, can take place in that the bore in the flange 6 and the control disk 4 are designed with correspondingly narrow tolerances for two of the screws 17.
  • the impeller 13 rotates with vanes 14, which is fastened on the shaft end 15 and can be adjusted in the longitudinal direction by means of the screw 16, in order to maintain the intended play with respect to the control disk 4 and the housing wall 7 remote from the motor.
  • the shaft is mounted in a longitudinally fixed manner in the bearing 18 of the motor 1 near the pump. It is not recommended to close the motor 1 bearing away from the pump as a fixed bearing use, because otherwise thermal expansion of the motor shaft can affect the position of the impeller.
  • the mechanical seal the spring of which is supported on the impeller 13, is provided within the connection housing 3.
  • the deep-drawing process used for the production of the work area housing 5 requires that the housing edges at 9 and 11 turn out to be rounded. This can be taken into account in that the outer wing corner 10 is rounded or beveled accordingly. However, an embodiment is preferred in which the rounding of the housing corner 9 is turned out as far as is required by the impeller diameter in the course of the plan machining of the housing wall 10.
  • the vanes of the impeller can have a radial projection in the manner shown at 12.
  • this projection can be dispensed with practically without loss of efficiency if the radius 20 of the rounding 11 is made small enough so that the area of the gap 21 between the rounding 11, the control disk 4 and the line 22, which the cylindrical part of the housing 5 parallel to the outer edges of the wings 14 (ie approximately axially parallel) continues, is small enough. Since it is mainly the parts of this surface that are closer to the axis that are important in this context, the size of the inscribed circle 23 inscribed on this surface is chosen as the dimension, the diameter of which should not exceed the values specified above.
  • the original sheet metal thickness of the working space housing 5 is preferably approximately 4 mm with an impeller diameter of 125 mm and preferably approximately 6 mm with an impeller diameter of 210 mm.
  • a bore 24 is arranged in the control disc 4, which leads into a special space 25 of the connection housing. It is arranged in such a way that it is at least adjacent to line 22, but better - as shown in FIG. 2 - is at least partially radially outside of this line. Dirt particles that collect in the gap 21, together with part of the liquid, can leave the working space through the bore 24 and enter the space 25, in which they can be deposited or from which they can also be removed from time to time.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Gyroscopes (AREA)
EP94106156A 1993-09-16 1994-04-20 Pompe à anneau liquide Expired - Lifetime EP0644317B1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
CA002131081A CA2131081C (fr) 1993-09-16 1994-08-29 Pompe a essence a anneau liquide
AU71625/94A AU673761B2 (en) 1993-09-16 1994-08-31 Liquid ring gas pump
CZ19942184A CZ291259B6 (cs) 1993-09-16 1994-09-08 Jednostupňový kapalinokruľný plynový kompresor
US08/304,534 US5509789A (en) 1993-09-16 1994-09-12 Liquid ring pump having a sheet metal working chamber casing
JP21706994A JP3538234B2 (ja) 1993-09-16 1994-09-12 液体リングガスポンプ
MYPI94002450A MY111315A (en) 1993-09-16 1994-09-14 Liquid ring gas pump.
CN94115333A CN1035837C (zh) 1993-09-16 1994-09-15 液体环式气泵
SK1119-94A SK281523B6 (sk) 1993-09-16 1994-09-16 Jednostupňový kvapalinokrúžny plynový kompresor
TW083109028A TW257826B (fr) 1993-09-16 1994-09-30

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4331489A DE4331489A1 (de) 1993-09-16 1993-09-16 Flüssigkeitsringgaspumpe in Blockbauweise
DE4331489 1993-09-16

Publications (2)

Publication Number Publication Date
EP0644317A1 true EP0644317A1 (fr) 1995-03-22
EP0644317B1 EP0644317B1 (fr) 1997-03-05

Family

ID=6497871

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94106156A Expired - Lifetime EP0644317B1 (fr) 1993-09-16 1994-04-20 Pompe à anneau liquide

Country Status (7)

Country Link
EP (1) EP0644317B1 (fr)
AT (1) ATE149632T1 (fr)
DE (2) DE4331489A1 (fr)
DK (1) DK0644317T3 (fr)
ES (1) ES2101379T3 (fr)
GR (1) GR3023681T3 (fr)
TW (1) TW257826B (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825521A1 (de) * 1998-06-08 2000-01-27 Siemens Ag Flüssigkeitsringpumpe
DE19911683A1 (de) * 1999-03-09 2000-09-21 Hielscher Gmbh Ultraschall-Sonotrode
DE19913632A1 (de) * 1999-03-25 2000-10-05 Siemens Ag Flüssigkeitsringpumpe
WO2004109111A1 (fr) * 2003-05-26 2004-12-16 Luk Automobiltechnik Gmbh & Co. Kg Pompe à cellules en ailettes à pot en tôle d'acier emboutie

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2731451B1 (de) * 1977-07-12 1978-04-13 Siemens Ag Fluessigkeitsringverdichter oder vakuumpumpe
EP0159968A2 (fr) * 1984-04-24 1985-10-30 CORINT S.r.l. Pompe pneumatique à palettes avec carter en tôle métallique estampée
EP0389838A2 (fr) * 1989-03-30 1990-10-03 Inoxpa, S.A. Carter pour pompe rotative

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4921705A (fr) * 1972-06-21 1974-02-26

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2731451B1 (de) * 1977-07-12 1978-04-13 Siemens Ag Fluessigkeitsringverdichter oder vakuumpumpe
EP0159968A2 (fr) * 1984-04-24 1985-10-30 CORINT S.r.l. Pompe pneumatique à palettes avec carter en tôle métallique estampée
EP0389838A2 (fr) * 1989-03-30 1990-10-03 Inoxpa, S.A. Carter pour pompe rotative

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825521A1 (de) * 1998-06-08 2000-01-27 Siemens Ag Flüssigkeitsringpumpe
DE19825521C2 (de) * 1998-06-08 2000-05-04 Siemens Ag Flüssigkeitsringpumpe
DE19911683A1 (de) * 1999-03-09 2000-09-21 Hielscher Gmbh Ultraschall-Sonotrode
DE19913632A1 (de) * 1999-03-25 2000-10-05 Siemens Ag Flüssigkeitsringpumpe
DE19913632C2 (de) * 1999-03-25 2001-02-08 Siemens Ag Flüssigkeitsringpumpe
WO2004109111A1 (fr) * 2003-05-26 2004-12-16 Luk Automobiltechnik Gmbh & Co. Kg Pompe à cellules en ailettes à pot en tôle d'acier emboutie

Also Published As

Publication number Publication date
GR3023681T3 (en) 1997-09-30
DE4331489A1 (de) 1995-03-23
EP0644317B1 (fr) 1997-03-05
TW257826B (fr) 1995-09-21
ES2101379T3 (es) 1997-07-01
ATE149632T1 (de) 1997-03-15
DK0644317T3 (da) 1997-09-22
DE59401906D1 (de) 1997-04-10

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