EP2587065B1 - Compresseur à anneau liquide - Google Patents

Compresseur à anneau liquide Download PDF

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Publication number
EP2587065B1
EP2587065B1 EP20110186724 EP11186724A EP2587065B1 EP 2587065 B1 EP2587065 B1 EP 2587065B1 EP 20110186724 EP20110186724 EP 20110186724 EP 11186724 A EP11186724 A EP 11186724A EP 2587065 B1 EP2587065 B1 EP 2587065B1
Authority
EP
European Patent Office
Prior art keywords
part section
curvature
rotation
liquid ring
point
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
EP20110186724
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German (de)
English (en)
Other versions
EP2587065A1 (fr
Inventor
Peter Bucher
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.)
Pompetravaini Nsb AG
Original Assignee
NSB Gas Processing AG
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 NSB Gas Processing AG filed Critical NSB Gas Processing AG
Priority to EP20110186724 priority Critical patent/EP2587065B1/fr
Priority to PCT/EP2012/071101 priority patent/WO2013060754A2/fr
Publication of EP2587065A1 publication Critical patent/EP2587065A1/fr
Application granted granted Critical
Publication of EP2587065B1 publication Critical patent/EP2587065B1/fr
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Classifications

    • 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
    • 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
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C2250/00—Geometry
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the invention relates to a liquid ring compressor according to the preamble of claim 1.
  • the publication EP 0 565 232 B1 discloses in Figure 11 a two-stage liquid ring compressor, wherein the two stages are arranged one after the other in the direction of rotation, so that the liquid ring compressor has two circumferentially spaced compression zones.
  • the liquid ring compressor has an elliptically extending housing, within which the rotor of the pump is arranged. This liquid ring compressor has the disadvantage that its efficiency is not optimal.
  • the object of the invention is to form an economically advantageous liquid ring compressor, which in particular has an improved efficiency.
  • a liquid ring compressor comprising a ring housing and a paddle wheel, wherein the paddle wheel is arranged within the ring housing and is rotatably mounted about a rotation axis and in a rotational direction, wherein the paddle wheel has a plurality of spaced apart in the direction of rotation blades, and wherein the ring housing has a circumferentially extending housing inner wall oriented toward the paddle wheel, the housing inner wall having a first section and a third section which are curved with respect to the axis of rotation, preferably circular and with an eccentricity radius of curvature, and which are mutually symmetrical with respect to the axis of rotation are arranged extending, and wherein the housing inner wall has a second portion which connects the first portion to the third portion, and wherein the second portion between the first subsection and the third subsection has an eccentricity point which has a maximum distance in a direction radial to the axis of rotation with respect to a circular path defined by the outer edges of the blades, and where
  • the profile of the housing inner wall of the inventive liquid ring compressor has the advantage that the ejection in the region of the outlet opening takes place more advantageously.
  • the volume of the liquid ring compressor in the region of the outlet opening in the direction of rotation is increasingly reduced, with the result that the liquid to be pumped by the liquid ring compressor experiences an increase in pressure in the region of the outlet opening, so that the fluid to be pumped at a higher pressure toward the outlet opening is encouraged.
  • the housing inner wall of the inventive liquid ring compressor is designed such that the suction of the liquid ring compressor in the inlet opening in the direction of rotation additionally increases, with the result that the liquid ring compressor has a larger intake volume, so that a larger amount of fluid to be pumped enters the intake volume via the inlet opening.
  • the inventive liquid ring compressor could also be called or used as a liquid ring pump, liquid ring vacuum pump or liquid ring compressor or liquid ring vacuum compressor.
  • Fig. 1 shows a section through a liquid ring compressor according to the invention 1.
  • the liquid ring compressor 1 comprises a liquid ring compressor housing 2 with an interior 2a, wherein in the interior 2a a rotatable impeller 4 is arranged, wherein the impeller 4 has a plurality of circumferentially spaced apart blades 4a, and wherein the impeller 4 is rotatably mounted about a center of rotation 4b.
  • a fixed inlet and outlet device 6 is arranged, which has two circumferentially extending inlet openings 7 and two circumferentially extending outlet openings 8.
  • the inlet and outlet device 6 is also referred to as internal distributor.
  • the liquid ring compressor 1 is configured in the illustrated embodiment as a double-flow pump by having these two inlet openings 7, two outlet openings 8 and also two mutual compression spaces 10a.
  • the interior 2a is bounded in the circumferential direction by a housing inner wall 3, which surrounds the impeller 4 in the circumferential direction from the outside, wherein the housing inner wall 3 is aligned to the impeller 4 out.
  • the housing inner wall 3 comprises a plurality of subsections 3a - 3n, which together form the in Form the circumferential direction of the housing inner wall 3.
  • In the interior 2a is a liquid which is conveyed by the impeller 4 in the direction of rotation 5, and which forms a liquid ring 9 with a boundary line 9a.
  • the space between the boundary line 9a and the inlet and outlet device 6 forms a delivery chamber 10, within which a gas is pumped from the inlet opening 7 to the outlet opening 8.
  • the delivery space 10 is divided in the circumferential direction into a plurality of sub-conveying spaces 10a which are successively delimited by a respective bucket 4a, wherein the volume of the sub-conveying spaces 10a increases in the area of the inlet opening 7 in the direction 9b and thereby performs a suction movement, and wherein reduces the volume of the sub-conveying spaces 10a toward the outlet opening 8 in the direction 9c, whereby a compression movement is carried out.
  • This pumping process takes place both in the FIG. 1
  • the housing inner wall 3 has a first section 3d and a third section 3f, which run concentric to the center of rotation 4b of the impeller 4 and the center of rotation 4b a distance R or a radius of excision R e , also referred to as Exzentrizticianskrümmungsradius R e .
  • a second subsection 3e extends between the first subsection 3d and the third subsection 3f.
  • a fourth subsection 3g extends between the third subsection 3f and the first subsection 3d.
  • the housing inner wall 3 has at the transitions of the sections 3d, 3e, 3f, 3g each have a kink K1, K2, K3, K4 on. These can be edged, angular or rounded.
  • the liquid ring compressor 1 has a first center 11a and a second center 11b, which are spaced by the same length with respect to the center of rotation 4b of the impeller 4.
  • the dashed line 11c shows a circle with first center 11a and eccentricity radius R e .
  • the dashed line 11d shows a circle with the second center 11b and the eccentricity radius R e .
  • the housing inner wall 3 also has two opposite eccentricity points 3h, at which the housing inner wall 3 has the greatest distance with respect to the center of rotation 4b.
  • the housing inner wall 3 runs along the second part section 3e such that the second part section 3e has no kinks, and that the second part section 3e has sections with different radii of curvature.
  • This configuration of the course of the housing inner wall 3 has the consequence that the suction movement 9b of the boundary line 9a is increased or increased, and that the compression movement 9c of the boundary line 9a is increased or amplified, resulting in an increase in the pumping capacity of the liquid ring compressor 1 result.
  • the radii Ri, Rk, Rl, Rm can vary in the circumferential direction. In a further advantageous embodiment, however, each of the radii Ri, Rk, Rl, Rm may also have a constant value.
  • FIG. 2 shows in a section perpendicular to the axis of rotation 4b, a further embodiment of a liquid ring compressor 1 with housing 2 and housing inner wall 3, wherein the liquid ring pump 1 is out of operation and therefore in the interior of the liquid ring compressor 1 no fluid.
  • the liquid ring compressor 1 has, as ready in FIG. 1 described, a housing inner wall 3 with circumferentially successively arranged first, second, third and fourth section 3d, 3e, 3f, 3g and arranged therebetween kinks or transition areas K1, K2, K3, K4.
  • all four radii Ri, Rk, Rl, Rm in the subsection 3e have a constant value.
  • the two radii Rm and Ri are larger than the eccentricity radius R e , whereas the two radii Rk and Rl are smaller than the eccentricity radius R e .
  • the portion 3e no kinks, which means that the sections with radii Rl, Rm, Ri, Rk at their transition points u 1, 3h and u4 in the direction of rotation 5 are mutually tangential, so that these transition points u 1, 3h and u4 have no kink or discontinuity.
  • FIG. 3 shows a detail view of the left upper part of in FIG. 2
  • the second section 3e comprises the following four sections successively in the direction of rotation 5, a seventh section 31 with radius of curvature R1, an eighth section 3m with radius of curvature Rm, which follows the junction u4, a fifth section 3i with radius of curvature Ri, which follows after the eccentricity point 3h, and a sixth Subsection 3k with radius of curvature Rk, which follows after the transition point u 1.
  • the second section 3e is mirror-symmetrical with respect to an axis passing through the points 3h and 4b.
  • the circular path K represents the circle described by the outer edge (4c) of the blades 4a of the blade wheel 4.
  • the distance A between the circular path K and the housing inner wall 3 increases from the region of the opening point 7a of the inlet opening 7 in the direction of rotation 5, and points in Eccentricity point 3h the highest value A1.
  • the distance A then reduces to the region of the closing point 8b of the outlet opening eighth FIG. 3 also shows the circular line 11c, which is defined by a circle with eccentricity radius R e and the first center 11a.
  • the housing inner wall 3 now runs along the fifth and sixth subsection 3i, 3k in such a way that the radius of curvature Ri has a greater value than the eccentricity radius R e , so that the fifth subsection 3i moves further away from the circular line 11c, and that the radius of curvature Rk is smaller Has value as the eccentricity radius R e , so that the sixth portion 3k of the circular line 11c approaches again.
  • the sixth section 3k is in an advantageous embodiment as in FIG. 3 represented along the outlet opening 8 arranged to effect through the course of the housing inner wall 3 along the sixth section 3k an increased compression movement 9c on the liquid ring 9 or on its boundary line 9a, thereby increasing the conveying effect to the outlet port 8 out.
  • FIG. 4 shows a further embodiment of a course of the housing inner wall 3.
  • the left half of the second section 3e is shown, which is a fifth Part 3i and a sixth section 3k includes.
  • the fifth section 3i has a radius of curvature Ri with a center of rotation zi.
  • the sixth section 3k has a radius of curvature Rk with a center of rotation zk.
  • the radii Ri, Rk and the centers of rotation zi, zk are dimensioned and arranged such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1, so that the transition point u1 has no kink or discontinuity.
  • the radii of curvature Ri, Rk could also have varying values in the direction of rotation 5, preferably such that the radii Ri are greater than R and that the radii Rk are smaller than R, and preferably such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1.
  • FIG. 5 shows a partial view of a section through the in FIG. 1 shown liquid ring compressor 1 along the section line BB. From this, the course of the blade wheel 4 with blade 4a within the housing 2 can be seen.

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

Claims (10)

  1. Compresseur à anneau liquide (1) comprenant un corps annulaire (2) ainsi qu'une roue à aubes (4), laquelle roue à aubes (4) est disposée à l'intérieur du corps annulaire (2) et montée tournante autour d'un axe de rotation (4b) dans un sens de rotation (5), la roue à aubes (4) présentant une pluralité d'aubes (4a) espacées les unes des autres dans le sens de rotation (5), et le corps annulaire (2) présentant une paroi intérieure de corps (3) dirigée vers la roue à aubes (4) et s'étendant en direction circonférentielle, caractérisé en ce que la paroi intérieure de corps (3) présente une première portion (3d) et une troisième portion (3f) qui s'étendent selon un tracé courbe, de préférence circulaire, par rapport à l'axe de rotation (4b) et avec un rayon de courbure d'excentricité (Re), et qui sont disposées l'une en face de l'autre et de manière à s'étendre symétriquement l'une à l'autre par rapport à l'axe de rotation (4b), et la paroi intérieure de corps (3) présentant une deuxième portion (3e) qui relie la première portion (3d) à la troisième portion (3f), et la deuxième portion (3e) présentant entre la première portion (3d) et la troisième portion (3f) un point d'excentricité (3h) qui présente, dans la direction radiale par rapport à l'axe de rotation (4b), un éloignement maximal (A1) par rapport à une trajectoire circulaire (K) définie par les bords extérieurs (4c) des aubes (4a), et la deuxième portion (3e) étant constituée, entre le point d'excentricité (3h) et la troisième portion (3f), dans le sens de rotation (5), d'une cinquième et d'une sixième portion (3i, 3k), la cinquième portion (3i) s'étendant selon un tracé courbe avec des rayons de courbure (Ri) qui sont plus grands que le rayon de courbure d'excentricité (Re) de la première portion (3d), et la sixième portion (3k) présentant un tracé courbe avec des rayons de courbure (Rk) qui sont plus petits que le rayon de courbure d'excentricité (Re) de la première portion (3d), la cinquième et la sixième portion (3i, 3k) s'étendant tangentiellement l'une à l'autre à leur point de transition (U1), et un dispositif d'entrée et de sortie (6) étant disposé à l'intérieur du corps annulaire (2), lequel présente une ouverture de sortie (8), et l'ouverture de sortie (8) s'étendant dans le sens de rotation (5) à l'intérieur de la zone comprise entre le point d'excentricité (3h) et la troisième portion (3f).
  2. Compresseur à anneau liquide (1) selon la revendication 1, caractérisé en ce que la cinquième portion (3i) présente un rayon de courbure constant (Ri) et/ou que la sixième portion (3k) présente un rayon de courbure constant (Rk).
  3. Compresseur à anneau liquide (1) selon l'une des revendications précédentes, caractérisé en ce que l'ouverture de sortie (8) s'étend le long de la même zone angulaire que la sixième portion (3k).
  4. Compresseur à anneau liquide (1) selon l'une des revendications précédentes, caractérisé en ce que la deuxième portion (3e) est constituée, entre la première portion (3d) et le point d'excentricité (3h), dans le sens de rotation (5), d'une septième et d'une huitième portion (31, 3m), la septième portion (31) présentant un tracé courbe avec des rayons de courbure (R1) qui sont plus petits que le rayon de courbure d'excentricité (Re) de la première portion (3d), et la huitième portion (3m) présentant un tracé courbe avec des rayons de courbure (Rm) qui sont plus grands que le rayon de courbure d'excentricité (Re) de la première portion (3d), et la septième et la huitième portion (31, 3m) s'étendant tangentiellement l'une à l'autre à leur point de transition (U2).
  5. Compresseur à anneau liquide (1) selon la revendication 4, caractérisé en ce que la septième portion (31) présente un rayon de courbure constant (R1) et/ou que la huitième portion (3m) présente un rayon de courbure constant (Rm).
  6. Compresseur à anneau liquide (1) selon l'une des revendications 4 ou 5, caractérisé en ce que la huitième et la cinquième portions (3m, 3i) s'étendent tangentiellement l'une à l'autre à leur point de transition, le point d'excentricité (3h).
  7. Compresseur à anneau liquide selon l'une des revendications 1 ou 2, caractérisé en ce que la deuxième portion (3e) présente, entre la première portion (3d) et le point d'excentricité (3h), dans le sens de rotation (5), toujours le même rayon de courbure.
  8. Compresseur à anneau liquide selon l'une des revendications 1 à 3, caractérisé en ce que le rayon de courbure de la deuxième portion (3e) correspond, entre la première portion (3d) et le point d'excentricité (3h), dans le sens de rotation (5), au rayon de courbure d'excentricité (Re) de la première portion (3d).
  9. Compresseur à anneau liquide selon l'une des revendications précédentes, caractérisé en ce que la transition de la sixième portion (3k) à la troisième portion (3f) présente un point d'inflexion (K1).
  10. Compresseur à anneau liquide selon l'une des revendications précédentes, caractérisé en ce que la paroi intérieure de corps (3) présente une quatrième portion (3g) qui relie, dans le sens de rotation (5), la troisième portion (3f) à la première portion (3d), et que la quatrième portion (3g) présente, par rapport à l'axe de rotation (4b), une symétrie de révolution par rapport à la deuxième portion (3e).
EP20110186724 2011-10-26 2011-10-26 Compresseur à anneau liquide Active EP2587065B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20110186724 EP2587065B1 (fr) 2011-10-26 2011-10-26 Compresseur à anneau liquide
PCT/EP2012/071101 WO2013060754A2 (fr) 2011-10-26 2012-10-25 Compresseur annulaire de liquides

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20110186724 EP2587065B1 (fr) 2011-10-26 2011-10-26 Compresseur à anneau liquide

Publications (2)

Publication Number Publication Date
EP2587065A1 EP2587065A1 (fr) 2013-05-01
EP2587065B1 true EP2587065B1 (fr) 2014-06-04

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EP20110186724 Active EP2587065B1 (fr) 2011-10-26 2011-10-26 Compresseur à anneau liquide

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EP (1) EP2587065B1 (fr)
WO (1) WO2013060754A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2540754A (en) * 2015-07-22 2017-02-01 Edwards Ltd Abatement system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1021976B (de) * 1951-02-15 1958-01-02 Nash Engineering Co Fluessigkeitsring-Gaspumpe
FR1388967A (fr) * 1964-01-02 1965-02-12 Perfectionnements aux pompes à gaz et compresseurs à anneau liquide
US5213479A (en) 1992-04-09 1993-05-25 The Nash Engineering Company Liquid ring pumps with improved housing shapes

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WO2013060754A3 (fr) 2013-09-26
EP2587065A1 (fr) 2013-05-01
WO2013060754A2 (fr) 2013-05-02

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