WO2013060754A2 - Compresseur annulaire de liquides - Google Patents

Compresseur annulaire de liquides Download PDF

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Publication number
WO2013060754A2
WO2013060754A2 PCT/EP2012/071101 EP2012071101W WO2013060754A2 WO 2013060754 A2 WO2013060754 A2 WO 2013060754A2 EP 2012071101 W EP2012071101 W EP 2012071101W WO 2013060754 A2 WO2013060754 A2 WO 2013060754A2
Authority
WO
WIPO (PCT)
Prior art keywords
section
curvature
rotation
eccentricity
partial section
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/EP2012/071101
Other languages
German (de)
English (en)
Other versions
WO2013060754A3 (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.)
NSB Gas Processing 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
Publication of WO2013060754A2 publication Critical patent/WO2013060754A2/fr
Publication of WO2013060754A3 publication Critical patent/WO2013060754A3/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
    • 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.
  • Liquid ring compressor has two circumferentially spaced compression zones.
  • Liquid ring compressor has an elliptical 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 disposed within the ring housing and is rotatably mounted about a rotational axis and in a rotational direction, wherein the paddle wheel has a plurality of spaced apart in the rotational direction blades, and wherein the annular housing one towards the paddle wheel aligned, extending in the circumferential direction housing inner wall, wherein the housing inner wall has a first portion and a third portion which is curved with respect to the axis of rotation, preferably circular and with a
  • Exzentizticianskrümmungsradius extend, and which are arranged opposite to the axis of rotation and mutually symmetrical, 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 portion and the third portion of a
  • the second subsection between the eccentricity point and the third subsection in the direction of rotation consists of a fifth and a sixth subsection, the fifth subsection having a curved course having radii of curvature greater than the eccentricity curvature radius of the first subsection, and wherein the sixth subsection has a curved course with radii of curvature smaller than that
  • Ring housing an inlet and outlet device is arranged, which has an outlet opening, wherein the outlet opening extends in the direction of rotation within the range between the eccentricity point and the third section.
  • Liquid ring compressor in the area of the outlet opening in
  • Liquid ring compressor designed such that the
  • Suction volume has, so that a larger amount of the fluid to be pumped passes through the inlet opening into the intake volume.
  • the inventive liquid ring compressor could also be used as a liquid ring pump, liquid ring vacuum pump or
  • Liquid ring compressor or liquid ring vacuum compressor referred to or used.
  • Fig. 1 is a perpendicular to the axis of the impeller cutting section through a liquid ring compressor comprising a
  • FIG. 3 is a detail view of the left part of the liquid ring compressor shown in FIG. 2;
  • Fig. 4 is a detail view of another embodiment of a
  • Fig. 5 is a section through Figure 1 along the section line B-B. Basically, the same parts are given the same reference numerals in the drawings.
  • the liquid ring compressor 1 comprises a liquid ring compressor housing 2 having a
  • 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 shown in the
  • Embodiment designed 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
  • the housing inner wall 3 encloses, wherein the housing inner wall 3 is aligned with the impeller 4 out.
  • the housing inner wall 3 comprises a plurality of subsections 3a - 3n, which together form the in - -
  • Border 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 chamber 10 is divided in the circumferential direction in a plurality of successively following and each by a blade 4a mutually limited Operafinisko 10 a, wherein the volume of
  • Partial delivery 10a enlarged in the region of the inlet opening 7 in the direction 9b and thereby performs a suction movement, and wherein the volume of the partial delivery spaces 10a to the outlet opening 8 toward 9c reduced, whereby a compression movement is performed.
  • This pumping process takes place both in the delivery chamber 10 shown at the top left in FIG
  • the housing inner wall 3 has a first section 3d and a third section 3f, which run concentrically to the center of rotation 4b of the paddle wheel 4 and to the center of rotation 4b a distance R
  • 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
  • the housing inner wall 3 has at the transitions of the sections 3d, 3e, 3f, 3g in each case a kink Kl, K2, K3, K4 - -
  • the liquid ring compressor 1 has a first center I Ia and a second center I Ib, which with respect to the
  • the dotted line 1 1c shows a circle with the first center I Ia and eccentricity radius R e .
  • the dotted line 1 ld shows a circle with the second center I Ib and eccentricity radius R e .
  • the housing inner wall 3 also has two opposite
  • Eccentricity points 3h at which the housing inner wall 3 with respect to the center of rotation 4b has the greatest distance.
  • the housing inner wall 3 extends along the second section 3e such that the second
  • Part 3e has no kinks, and that the second section 3e has sections with different radii of curvature.
  • the housing inner wall 3 extends along the second subsection 3e in the region of the opening point 7a of the inlet opening 7 and / or in the region of the closing point 8b of the outlet opening 8
  • 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. - -
  • Figure 2 shows in a section perpendicular to the axis of rotation 4b, a further embodiment of a liquid ring compressor 1 with the housing 2 and the housing inner wall 3, wherein the
  • Liquid ring pump 1 out of service and is therefore in
  • the liquid ring compressor 1 has a housing inner wall 3 with first, second, third and fourth passages arranged successively in the circumferential direction
  • 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
  • the two radii Rk and Rl are smaller than the eccentricity radius R e .
  • the section 3e has no kinks, which means that the sections with radii Rl, Rm, Ri, Rk at their crossing points ul, 3h and u4 in
  • Rotation direction 5 are mutually tangential, so this
  • Transition points ul, 3h and u4 have no kink or discontinuity.
  • FIG. 3 shows a detail view of the upper left part of the liquid ring compressor 1 shown in FIG. 2.
  • the second part section 3e comprises the following four sections successively following one another in the direction of rotation 5, a seventh part section 31
  • Transition point ul follows.
  • 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 has in Exzentrizticianstician 3h the highest value AI. The distance A then reduces to the area of
  • Figure 3 also shows the circle line 1 1c, which is defined by a circle with eccentricity radius R e and the first center I Ia.
  • 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 is further away from the circular line 11c, and that the
  • Radius of curvature Rk has a smaller value than that
  • the sixth section 3k is arranged in an advantageous embodiment as shown in Figure 3 extending along the outlet opening 8 to cause by 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 action to the outlet opening 8.
  • Figure 4 shows a further embodiment of a course of the housing inner wall 3. In essence, 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
  • the sixth section 3k has a
  • Circular line 1 1c shown with eccentricity radius R e and center of rotation I Ia, as well as the circle line 4c dashed lines with center of rotation 4b of the impeller 4 and with eccentricity radius R e .
  • Turning centers zi, zk may be sized and arranged in a variety of ways, such that the tangents of the fifth and sixth sections 3i, 3k are identical at the transition location ul.
  • the radii of curvature Ri, Rk could be in
  • 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 ul.
  • FIG. 5 shows a partial view of a section through the liquid ring compressor 1 shown in FIG. 1 along the section line B - B. From this, the course of the blade wheel 4 with the blade 4a within the housing 2 can be seen.

Landscapes

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

Abstract

Le compresseur annulaire de liquides (1) selon l'invention comprend un carter annulaire (2) ainsi qu'une roue à aubes (4). La roue à aubes (4) est placée à l'intérieur du carter annulaire (2), et est montée rotative dans une direction de rotation (5) autour d'un axe de rotation (4b), la roue à aubes (4) comportant une pluralité d'aubes (4a) espacées les unes des autres, disposées dans le sens de la rotation, et le carter annulaire (2) présentant une paroi interne (3) s'étendant dans une direction périphérique. Ladite paroi interne (3) présente une première section (3d) et une troisième section (3f) qui s'étendent selon un tracé courbe, de préférence circulaire, avec un rayon de courbure d'excentricité (Re), et qui sont placées symétriquement l'une à l'autre relativement à l'axe de rotation (4b). La paroi interne (3) présente en outre une seconde section (3e) qui relie la première section (3d) à la troisième section (3f), et cette seconde section (3c) présente un point d'excentricité (3h) situé entre la première section (3d) et la troisième section (3f), ledit point d'excentricité présentant un éloignement maximal (A1) dans la direction radiale relativement à l'axe de rotation (4b) par rapport à une trajectoire circulaire (K) définie par les bords externes (4c) des aubes (4a). entre la première section (3d) et la troisième section (3f), et la seconde section (3a) étant constituée, entre le point d'excentricité (3h) et la troisième section (3f),dans la direction de rotation (5), d'une cinquième et d'une sixième section (3i, 3k), la cinquième section (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 section (3d), et la sixième section (3k) présentant un tracé courbe avec des rayons de courbure (Rk) plus petits que le rayon de courbure d'excentricité (Re) de la première section (3d), la cinquième et la sixième section (3i,3k) étant tangentielles l'une relativement à l'autre au niveau de leur point de transition (U1). Un dispositif d'entrée et de sortie (6) est en outre disposé à l'intérieur du carter annulaire (2), et comprend une ouverture de sortie (8), laquelle s'étend dans la zone comprise entre le point d'excentricité (3h) et la troisième section (3f) dans la direction de rotation (5).
PCT/EP2012/071101 2011-10-26 2012-10-25 Compresseur annulaire de liquides Ceased WO2013060754A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP11186724.8 2011-10-26
EP20110186724 EP2587065B1 (fr) 2011-10-26 2011-10-26 Compresseur à anneau liquide

Publications (2)

Publication Number Publication Date
WO2013060754A2 true WO2013060754A2 (fr) 2013-05-02
WO2013060754A3 WO2013060754A3 (fr) 2013-09-26

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PCT/EP2012/071101 Ceased WO2013060754A2 (fr) 2011-10-26 2012-10-25 Compresseur annulaire de liquides

Country Status (2)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118378314A (zh) * 2024-06-24 2024-07-23 淄博真空设备厂有限公司 液环压缩机叶轮设计方法

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

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0565232B1 (fr) 1992-04-09 1996-07-03 The Nash Engineering Company Carter pour pompe à anneau liquide

Family Cites Families (2)

* 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

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0565232B1 (fr) 1992-04-09 1996-07-03 The Nash Engineering Company Carter pour pompe à anneau liquide

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118378314A (zh) * 2024-06-24 2024-07-23 淄博真空设备厂有限公司 液环压缩机叶轮设计方法
CN118378314B (zh) * 2024-06-24 2024-08-20 淄博真空设备厂有限公司 液环压缩机叶轮设计方法

Also Published As

Publication number Publication date
WO2013060754A3 (fr) 2013-09-26
EP2587065B1 (fr) 2014-06-04
EP2587065A1 (fr) 2013-05-01

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