WO2013060754A2 - Liquid ring compressor - Google Patents

Abstract

The liquid ring compressor (1) comprises a ring housing (2) and a blade wheel (4), wherein the blade wheel (4) is arranged inside the ring housing (2) and is supported such as to be rotatable about an axis of rotation (4b) and in a direction of rotation (5), wherein the blade wheel (4) has a plurality of blades (4a) that are mutually spaced in the direction of rotation (5), and wherein the ring housing (2) has an inner housing wall (3) that is oriented toward the blade wheel (4) and that extends in the circumferential direction, wherein the inner housing wall (3) has a first partial section (3d) and a third partial section (3f), which are curved with respect to the axis of rotation (4b), preferably circularly, and extend with an eccentricity radius of curvature (R_e) and which are arranged opposite each other with respect to the axis of rotation (4b) and extend in symmetry with each other, and wherein the inner housing wall (3) has a second partial section (3e) that connects the first partial section (3d) to the third partial section (3f), and wherein the second partial section (3e) has an eccentricity point (3h) between the first partial section (3d) and the third partial section (3f), which eccentricity point has a maximum distance (A1) in a direction radial to the axis of rotation (4b) with respect to a circular path (K) defined by the outer edges (4c) of the blades (4a), and wherein the second partial section (3e), between the eccentricity point (3h) and the third partial section (3f) in the direction of rotation (5), consists of a fifth and a sixth partial section (3i, 3k), wherein the fifth partial section (3i) has a curved course having radii of curvature (R_i) that are greater than the eccentricity radius of curvature (R_e) of the first partial section (3d), and wherein the sixth partial section (3k) has a curved course having radii of curvature (R_k) that are less than the eccentricity radius of curvature (R_e) of the first partial section (3d), and wherein the fifth and sixth partial sections (3i, 3k) extend mutually tangentially at the transition point (U₁) thereof, and wherein an inlet and outlet device (6) is arranged within the ring housing (2), which inlet and outlet device has an outlet opening (8), and wherein the outlet opening (8) extends within the region between the eccentricity point (3h) and the third partial section (3f) in the direction of rotation (5).

Description

 LIQUID RING COMPRESSORS

description

The invention relates to a liquid ring compressor according to the preamble of claim 1.

State of the art

The document EP 0 565 232 Bl discloses in Figure 1 1 a two-stage liquid ring compressor, wherein the two stages are arranged one behind the other in the direction of rotation, so that the

Liquid ring compressor has two circumferentially spaced compression zones. Of the

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. - -

Presentation of the invention

The object of the invention is to form an economically advantageous liquid ring compressor, which in particular has an improved efficiency.

This object is achieved with a liquid ring compressor having the features of claim 1. The dependent claims 2 to 10 relate to further advantageous embodiments.

The problem is solved in particular with a

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

Exzentizitätskrümmungsradius 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

Exzentrizitätspunkt having in radial direction to the axis of rotation with respect to a circular path defined by the outer edges of the blades has a maximum distance, and wherein - -

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

Exzentrizitätskrümmungsradius of the first section, and wherein the fifth and sixth section at the transition point are mutually tangential, and wherein within the

 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. The in

The direction of rotation extending outlet opening extends

preferably along a portion of the area between the point of eccentricity and the third portion.

The course of the housing inner wall of the erfmdungsgemässen

Liquid ring compressor has the advantage that the

 Ejection in the region of the outlet opening takes place more advantageously. In an advantageous embodiment, the volume of

Liquid ring compressor in the area of the outlet opening in

Increasingly reduced direction of rotation, which has the consequence that the fluid to be pumped by the liquid ring compressor in the region of

Outlet opening experiences an increase in pressure, so that too

pumping fluid is conveyed to the outlet opening at a higher pressure. - -

In a further advantageous embodiment, the

Housing inner wall of the erfmdungsgemässen

Liquid ring compressor designed such that the

Intake space of the liquid ring compressor in the region of

Inlet opening in the direction of rotation additionally increased, with the result that the liquid ring compressor a larger

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.

The invention will be explained below with reference to exemplary embodiments in detail.

Brief description of the drawings

The used to explain the embodiments

Drawings show:

Fig. 1 is a perpendicular to the axis of the impeller cutting section through a liquid ring compressor comprising a

Housing and a rotor;

2 shows a section through a further embodiment of a

Liquid ring compressor;

FIG. 3 is a detail view of the left part of the liquid ring compressor shown in FIG. 2; FIG. - -

Fig. 4 is a detail view of another embodiment of a

Liquid ring compressor;

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.

1 shows a section through a erfmdungsgemässen

Liquid Ring Compressor 1. The liquid ring compressor 1 comprises a liquid ring compressor housing 2 having a

Interior 2a, wherein in the interior 2a a rotatable impeller 4 is arranged, wherein the impeller 4 has a plurality of in

Circumferentially having mutually spaced blades 4a, and wherein the paddle wheel 4 is rotatably mounted about a center of rotation 4b. In the center of the liquid ring compressor 1 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

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 - -

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

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. As shown in Figure 1, the delivery chamber 10 is divided in the circumferential direction in a plurality of successively following and each by a blade 4a mutually limited Teilförderräume 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

Part delivery chambers 10a as well as in the delivery chamber 10 and the sub-conveying spaces 10a shown at the bottom right instead. In the illustrated embodiment, 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

or an eccentricity radius R _e , also as

Exzentrizitätskrümmungsradius R _e designated having. 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

Part of section 3d. 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 - -

on. These can be edged, angular or rounded. The liquid ring compressor 1 has a first center I Ia and a second center I Ib, which with respect to the

Turning center 4b of the paddle wheel 4 are spaced by the same length. 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. In an advantageous embodiment, 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. In the most preferred embodiment, 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

Radii of curvature Rl, Rk, which is smaller than that

Exzentrizitätsradius R _e , whereas the second section 3e

between them radii of curvature Rm, Ri, which are greater than the eccentricity radius R _e . 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 increased, which is an enlargement of

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. - -

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

 Interior of the liquid ring compressor 1 no fluid is. As already described in FIG. 1, the liquid ring compressor 1 has a housing inner wall 3 with first, second, third and fourth passages arranged successively in the circumferential direction

Subsection 3d, 3e, 3f, 3g and arranged therebetween kinks or transition areas K1, K2, K3, K4. In this exemplary embodiment, 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 . In a preferred embodiment, 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

Radius of curvature Rl, an eighth section 3m with

Radius of curvature Rm, which follows after the transition point u4, a fifth portion 3i with radius of curvature Ri, which follows the point of eccentricity 3h, and a sixth - -

Subsection 3k with radius of curvature Rk, which after the

Transition point ul follows. In an advantageous embodiment, 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 Exzentrizitätspunkt 3h the highest value AI. The distance A then reduces to the area of

Closing point 8b of the outlet opening 8. 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

Exzentrizitätsradius R _e , so that the sixth section 3k of the circle line 1 1c approaches again. 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

Turning on zi. The sixth section 3k has a

Radius of curvature Rk with center of rotation zk on. 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 ul, so that the transition point ul has no kink or discontinuity. For better understanding, the dashed line in FIG

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 . The two

Curvature radii Ri, Rk have in the illustrated

Embodiment of a constant value, wherein Ri is greater than R and wherein Rk is less than R. The radii Ri, Rk and the

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

However, the direction of rotation 5 also have varying values,

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 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.

Claims

1. Liquid ring compressor (1) comprising a ring housing (2) and a paddle wheel (4), wherein the paddle wheel (4) within the ring housing (2) is arranged and about an axis of rotation (4b) and in a rotational direction (5) is rotatably mounted in that the paddle wheel (4) has a plurality of blades (4a) spaced apart from one another in the direction of rotation (5), and wherein the ring housing (2) has a circumferential housing inner wall (3) oriented towards the paddle wheel (4) the housing inner wall (3) has a first portion (3d) and a third portion (3f) curved with respect to the rotation axis (4b), preferably circular and with a radius of curvature of curvature (R _e ), and with respect to the rotation axis (4b) opposite and each other wherein the housing inner wall (3) has a second partial section (3e) which connects the first partial section (3d) to the third partial section (3f), and wherein the second partial section (3e) is arranged between the first partial section (3d ) and the third Partial section (3f) has an eccentricity point (3h) which has a maximum distance (AI) in a radial direction with respect to a circular path (K) defined by the outer edges (4c) of the blades (4a) in the radial direction (4b), and wherein the second Subsection (3e) between the Exzentrizitätspunkt (3h) and the third section (3f) in the direction of rotation (5) consists of a fifth and a sixth section (3i, 3k), wherein the fifth section (3i) a curved course having radii of curvature (Ri) which are greater than the eccentricity curvature radius (R _e ) of the first section (3d), and wherein the sixth section (3k) has a curved course with radii of curvature (Rk) which are smaller than the eccentricity radius of curvature (Rk) R _e ) of the first section (3d), and wherein the fifth and sixth section (3i, 3k) at their transition point (Ul) are mutually tangential, and wherein within the ring housing (2) an inlet and outlet device (6) is arranged which has an outlet opening (8), and wherein the outlet opening (8) extends in the direction of rotation (5) within the area between the point of eccentricity (3h) and the third section (3f). Liquid ring compressor (1) according to claim 1, characterized in that the fifth subsection (3i) has a constant radius of curvature (Ri) and / or that the sixth subsection (3k) has a constant radius of curvature (Rk). Liquid ring compressor (1) according to one of the preceding claims, characterized in that the outlet opening (8) extends along the same angular range as the sixth section (3k). Liquid ring compressor (1) according to one of the preceding claims, characterized in that the second Partial section (3e) between the first section (3d) and the eccentricity point (3h) in the direction of rotation (5) consists of a seventh and an eighth section (31, 3m), wherein the seventh section (31) has a curved course with radii of curvature (3). Rl) which are smaller than the Eccentricity radius of curvature (R _e ) of the first section (3d), and wherein the eighth section (3m) has a curved course with radii of curvature (Rm) which are greater than the eccentricity radius of curvature (R _e ) of the first section (3d), and wherein the seventh and respect Subsection (31.3m) at the transition point (U2) are mutually tangential. 5. Liquid ring compressor (1) according to claim 4, characterized in that the seventh section (31) has a constant radius of curvature (Rl) and / or that the eighth section (3m) has a constant radius of curvature (Rm). 6. liquid ring compressor (1) according to one of claims 4 or 5, characterized in that the eighth and the fifth section (3m, 3i) at the transition point, the Exzentrizitätspunkt (3h) are mutually tangential. 7. Liquid ring compressor according to one of claims 1 or 2, characterized in that the second section (3e) between the first section (3d) and the Exzentrizitätspunkt (3h) in the direction of rotation (5) constantly has the same radius of curvature. 8. Liquid ring compressor according to one of claims 1 to 3, characterized in that the radius of curvature of the second section (3e) between the first section (3d) and the eccentricity point (3h) in the direction of rotation (5) corresponds to the eccentricity curvature radius (R _e ) of the first section (3d). Liquid ring pump according to one of the preceding claims, that the transition from the sixth section (3k) to the third section (3f) has a kink (Kl). 10. Liquid ring compressor according to one of the preceding claims, characterized in that the housing inner wall (3) has a fourth section (3g) which connects the third section (3f) in the direction of rotation (5) with the first section (3d), and in that fourth section (3g) with respect to the axis of rotation (4b) rotationally symmetrical to the second section (3e) extends.