Radial compressor

Abstract

A radial compressor has at least one compressor stage. The compressor stage includes: an impeller having moving blades on a rotor side arranged in a flow channel of the compressor stage. The flow channel is bounded by a hub contour and a housing contour or cover disc contour. Each moving blade has a flow inlet edge and a flow outlet edge. In the region of the compressor stage on the hub contour of the flow channel, initially a curvature change from a first concave curvature into a convex curvature and following this a curvature change from the convex curvature into a second concave curvature is formed; and/or on the housing contour or cover disc contour of the flow channel, initially a curvature change from a first convex curvature into a concave curvature and following this a curvature change from the concave curvature into a second convex curvature is formed.

Claims

1. A radial compressor, with at least one compressor stage, wherein the, or each, compressor stage comprises: an impeller (10) having multiple moving blades (12) on a rotor side, which are arranged in a flow channel (11) of the at least one compressor stage, wherein: the flow channel (11) of the at least one compressor stage is bounded by a hub contour (13) and a housing contour or cover disc contour (14), each moving blade (12) has a flow inlet edge (15) and a flow outlet edge (16), in the region of the at least one compressor stage on the hub contour (13) of the flow channel (11), seen in a through-flow direction of the flow channel (11) initially there is arranged a curvature change from a first concave curvature into a convex curvature that is curved towards the inside into the flow channel (11) and reduces the flow cross section of the flow channel (11) and following this there is arranged a curvature change from the convex curvature into a second concave curvature; and on the housing contour or cover disc contour (14) of the flow channel (11), seen in the through-flow direction of the flow channel (11) initially there is arranged only one curvature change from a first convex curvature into a concave curvature that is curved towards the outside out of the flow channel (11) and increases the flow cross section of the flow channel (11) and following this there is arranged only one curvature change from the concave curvature into a second convex curvature, wherein 0% of a length LN of the hub contour (13) in meridional projection lies upstream of the flow inlet edge (15) of the moving blades (12) and 100% of a length LN of the hub contour (13) in meridional projection lies in a region of the flow outlet edge (16) of the moving blades (12) of the impeller wherein each curvature change is a smooth transition, and wherein the housing contour or cover disk contour (14) changes in curvature are annular features.

2. The radial compressor according to claim 1, wherein on the hub contour (13) of the flow channel (11) for a first concave curvature radius R1N and a second concave curvature radius R3N of the flow channel (11) the following relationship with an outer diameter D2 of the impeller (10) applies in each case:
0.05<R1N/D2<0.60,
0.05<R3N/D2<0.80.

3. The radial compressor according to claim 2, wherein on the hub contour (13) of the flow channel (11) for a convex curvature radius R2N of the flow channel (11) the following relationship with the outer diameter D2 of the impeller (10) applies:
0.10<R2N/D2<5.00.

4. The radial compressor according to claim 3, wherein on the hub contour (13) of the flow channel (11) the curvature change from the first concave curvature into the convex curvature lies in a range between 10.0% and 60.0% of the length of the hub contour (13) in meridional projection, and on the hub contour (13) of the flow channel (11) the curvature change from the convex curvature into the second concave curvature lies in a range between 15.0% and 75.0% of the length of the hub contour (13) in meridional projection.

5. A radial compressor, with at least one compressor stage, wherein the, or each, compressor stage comprises: an impeller (10) having multiple moving blades (12) on a rotor side, which are arranged in a flow channel (11) of the at least one compressor stage, wherein: the flow channel (11) of the at least one compressor stage is bounded by a hub contour (13) and a housing contour or cover disc contour (14), each moving blade (12) has a flow inlet edge (15) and a flow outlet edge (16), in the region of the at least one compressor stage on the hub contour (13) of the flow channel (11), seen in a through-flow direction of the flow channel (11) initially there is arranged a curvature change from a first concave curvature into a convex curvature that is curved towards the inside into the flow channel (11) and reduces the flow cross section of the flow channel (11) and following this there is arranged a curvature change from the convex curvature into a second concave curvature; and on the housing contour or cover disc contour (14) of the flow channel (11), seen in the through-flow direction of the flow channel (11) initially there is arranged only one curvature change from a first convex curvature into a concave curvature that is curved towards the outside out of the flow channel (11) and increases the flow cross section of the flow channel (11) and following this there is arranged only one curvature change from the concave curvature into a second convex curvature, wherein on the hub contour (13) of the flow channel (11) for a first concave curvature radius R1N and a second concave curvature radius R3N of the flow channel (11) the following relationship with an outer diameter D2 of the impeller (10) applies in each case:
0.05<R1N/D2<0.60,
0.05<R3N/D2<0.80, wherein on the hub contour (13) of the flow channel (11) for a convex curvature radius R2N of the flow channel (11) the following relationship with the outer diameter D2 of the impeller (10) applies:
0.10<R2N/D2<5.00, wherein on the hub contour (13) of the flow channel (11) the curvature change from the first concave curvature into the convex curvature lies in a range between 10.0% and 60.0% of the length of the hub contour (13) in meridional projection, and on the hub contour (13) of the flow channel (11) the curvature change from the convex curvature into the second concave curvature lies in a range between 15.0% and 75.0% of the length of the hub contour (13) in meridional projection, and wherein on the housing contour or cover disc contour (14) of the flow channel (11) for a first convex curvature radius R1D and a second convex curvature radius R3D of the flow channel (11) the following relationship with the outer diameter D2 of the impeller (10) applies in each case:
0.03<R1D/D2<0.11,
0.05<R3D/D2<0.52.

6. The radial compressor according to claim 5, wherein on the housing contour or cover disc contour (14) of the flow channel (11) for a concave curvature radius R2D of the flow channel (11) the following relationship with the outer diameter D2 of the impeller (10) applies:
0.05<R2D/D2<0.84.

7. The radial compressor according to claim 6, wherein on the housing contour or cover disc contour (14) of the flow channel (11) the curvature change from the first convex curvature into the concave curvature lies in a range between 0.0% and 25% of the length of the housing contour or cover disc contour (14) in meridional projection, and on the housing contour or cover disc contour (14) of the flow channel (11) the curvature change from the concave curvature into the second convex curvature lies in a range between 10.0% and 60.0% of the length of the housing contour or cover disc contour (14) in meridional projection.

8. The radial compressor according to claim 7, wherein in the region of the respective compressor stage at least two of the following relationships apply:
0.15<D1/D2<0.60,
0.20<D3/D2<0.94,
0.05<L1/D2<0.35,
0.01<L2/D2<0.15,
20<<+90, wherein D1 is a hub diameter of the impeller (10), D3 is a suction mouth diameter of the impeller (10), D2 is the outer diameter of the impeller (10), L1 is an axial length of the housing contour (14) or cover disc contour of the flow channel (11) on the stator side, L2 is an axial length of the flow outlet edge (16) of the moving blades (12) of the impeller (10) and a is an angle of inclination of the flow inlet edge (15) of the moving blades (12) of the impeller (10).

9. The radial compressor according to claim 8, wherein the outer diameter D2 of the impeller (10) of the at least one compressor stage is between 30 mm and 2,500 mm.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Preferred further developments of the invention are obtained from the following description. Exemplary embodiments of the invention are explained in more detail with the help of the drawing without being restricted to this. In the drawings:

(2) FIG. 1: is a detail of a radial compressor according to the invention in meridional section for explaining design parameters of the radial compressor; and

(3) FIG. 2: is a detail for explaining further design parameters of the radial compressor.

DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS

(4) The present invention relates to a radial compressor with at least one compressor stage. FIGS. 1 and 2 show a detail of a radial compressor according to an exemplary embodiment of the invention in the region of a compressor stage in meridional section. The, or each, compressor stage of the radial compressor according to the invention comprises an impeller 10 with multiple moving blades 12 on the rotor side arranged in a flow channel 11 of the respective compressor stage. The flow channel 11 of the respective compressor stage is bounded by a hub contour 13 on the rotor side and a housing contour 14 on the stator side or a cover disc contour 14 on the rotor side. Each moving blade 12 has a flow inlet edge 15 and a flow outlet edge 16.

(5) In FIGS. 1 and 2, various design parameters of the compressor stage shown there are entered, namely the hub diameter D1 of the respective impeller 10, the suction mouth diameter D2 of the respective impeller 10, the outer diameter D2 of the respective impeller 10, the axial length L1 of the housing contour or cover disc contour 14 of the respective flow channel 11, the axial length L2 of the flow outlet edge 16 of the moving blades of the respective impeller 10 and the angle of inclination a of the flow inlet edge 15 of the moving blades 12 of the respective impeller 10 to the radial direction of the same.

(6) Furthermore, a first concave curvature R1N, a convex curvature radius R2N and a second concave curvature radius R3N of the hub contour 13 of the respective flow channel 11 are entered in FIG. 1 as design parameters of the compressor stage shown there.

(7) In FIG. 2, a first convex curvature radius R1D, a concave curvature radius R2D and a second convex curvature radius R3D of the housing contour or cover disc contour 14 of the respective flow channel 11 are additionally entered.

(8) In the disclosed embodiments of the invention, initially a curvature change from a first concave curvature into a convex curvature, and following this a curvature change from the convex curvature into a second concave curvature, is formed in the region of at least one compressor stage on the hub contour 13 of the respective flow channel 11 on the rotor side seen in a through-flow direction of the respective flow channel 11. Alternatively or preferentially in addition, initially a curvature change from a first convex curvature into a concave curvature, and following this a curvature change from the concave curvature into a second convex curvature, is formed on the housing contour or cover disc contour 14 of the respective flow channel 11 seen in through-flow direction of the respective flow channel 11. Through the above curvature changes on the hub contour 13 and/or on the housing contour or cover disc contour 14 the moving blade loading of the respective impeller 10 can be equalized. The equalization of the moving blade loading on the respective impeller reduces the risk of a flow separation and can with the working range remaining the same provide an increase of the efficiency.

(9) On the hub contour 13 of the respective flow channel 11 the curvature change from the first concave curvature into the convex curvature lies in a range between 10.0% and 60.0% of the length LN of the hub contour in meridional projection, wherein on the hub contour 13 of the respective flow channel 11 the curvature change from the convex curvature into the second concave curvature lies in a range between 15.0% and 75.0% of the length LN of the hub contour in meridional projection.

(10) 0% of the length LN of the hub contour 13 in meridional projection lies upstream of the flow inlet edge 15 of the moving blades 12 and 100% of the length LN of the hub contour 13 in meridional projection lies in the region of the flow outlet edge 16 of the moving blades 12 of the respective impeller.

(11) Preferably, the curvature change from the first concave curvature into the convex curvature lies in a range between 16.0% and 46.0% of the length of the hub contour 13 in meridional projection and the curvature change from the convex curvature into the second concave curvature in a range between 30.0% and 65.0% of the length of the hub contour in meridional projection. These design parameters are preferred in particular when the respective flow channel 11 is bounded by a hub contour 13 on the rotor side and a cover disc contour 14 on the rotor side, i.e., in the case of so-called closed radial compressors.

(12) On the housing contour or cover disc contour 14 of the respective flow channel 11 the curvature change from the first convex curvature into the concave curvature lies in a range between 0.0% and 25.0% of the length LD of the housing contour or cover disc contour 14 in meridional projection, wherein on the housing contour or cover disc contour 14 of the respective flow channel 11 the curvature change from the concave curvature into the second convex curvature lies in a range between 10.0% and 60.0% of the length LD of the housing contour or cover disc contour 14 in meridional projection.

(13) 0% of the length LD of the housing contour or cover disc contour 14 in meridional projection lies upstream of the flow inlet edge 15 of the moving blades 12 and 100% of the length LD of the housing contour or cover disc contour 14 in meridional projection lies in the region of the flow outlet edge 16 of the moving blades 12 of the respective impeller.

(14) Preferably, the curvature change from the first convex curvature into the concave curvature lies in a range between 5.0% and 9.0% of the length of the housing contour or cover disc contour 14 in meridional projection and the curvature change from the concave curvature into the second convex curvature in a range between 21.0% and 35.0% of the length of the housing contour or cover disc contour in meridional projection. These design parameters are preferred with so-called closed radial compressors.

(15) On the hub contour 13 of the respective flow channel 11 of the respective impeller 10 on the rotor side the following applies:
0.05<R1N/D2<0.60,
0.05<R3N/D2<0.80,
0.10<R2N/D2<5.00.

(16) Preferably, in the case of so-called closed radial compressors the following applies on the hub contour 13 of the respective flow channel 11 of the respective impeller 10 on the rotor side:
0.08<R1N/D2<0.53,
0.15<R3N/D2<0.39,
0.75<R2N/D2<3.35.

(17) On the housing contour 14 or cover disc contour of the respective flow channel 11 of the respective impeller 10 on the stator side the following applies:
0.03<R1D/D2<0.11,
0.05<R3D/D2<0.52,
0.05<R2D/D2<0.84

(18) Preferably, in the case of so-called closed radial compressors, the following applies on the housing contour 14 or cover disc contour of the respective flow channel 11 of the respective impeller 10 on the stator side:
0.06<R1D/D2<0.09,
0.15<R3D/D2<0.25,
0.34<R2D/D2<0.56.

(19) In the region of the respective compressor stage, at least two, preferentially at least three, particularly preferably at least four, most preferably all of the following relationships apply:
0.15<D1/D2<0.60,
0.20<D3/D2<0.94,
0.05<L1/D2<0.35,
0.01<L2/D2<0.15,
20<<+90.

(20) Preferably, in the case of so-called close radial compressors, at least two, preferentially at least three, particularly preferably at least four, most preferably all of the following relationships apply in the region of the respective compressor stage:
0.23<D1/D2<0.50,
0.47<D3/D2<0.94,
0.11<L1/D2<0.23,
0.04<L2/D2<0.09,
0<<+70.

(21) The outer diameter D2 of the impeller 10 of the respective compressor stage amounts to between 30 mm and 2,500 mm.

(22) By providing the convex curvature and the above curvature change on the hub contour 13 and/or by providing the concave curvature and the above curvature change on the housing contour or cover disc contour 14 the moving blade loading can be equalized. The equalization of the moving blade loading reduces the danger of a flow separation and can with the working range remaining the same provide an increase of the efficiency.

(23) On the hub contour 13, the convex curvature subject to reducing the flow cross section of the flow channel 11 is curved towards the inside into the flow channel 11. On the housing contour or cover disc contour 14, the concave curvature subject to increasing the flow cross section of the flow channel 11 is curved towards the outside out of the flow channel 11.

(24) Thus, while there have been shown and described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements and/or method steps which perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements and/or method steps shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.