Radial Turbomachine

Abstract

A radial turbomachine has a first housing part and a second housing part, which jointly form and delimit a flow channel. The first housing part forms a motor chamber for accommodating a drive motor, and the second housing part forms a gas inlet. Furthermore, a radial impeller is provided, which can be driven about an axis of rotation by the drive motor in order to suction a gas from outside the turbomachine through the gas inlet into the flow channel and to convey said gas out of the flow channel through a gas outlet to the outside. The first housing part or the second housing part forms the gas outlet at a radial distance from the axis of rotation and peripherally delimits the gas outlet.

Claims

1. A radial turbomachine comprising, a first housing part which forms a motor chamber for accommodating a drive motor, a second housing part which forms a gas inlet; a flow channel which is jointly formed and delimited by the first housing part and the second housing part; a gas outlet; and a radial impeller which driveable about an axis of rotation by the drive motor in order to suction a gas from outside the turbomachine through the gas inlet into the flow channel and to convey said gas out of the flow channel through the gas outlet to the outside, wherein the first housing part or the second housing part forms the gas outlet at a radial distance from the axis of rotation and circumferentially delimits the gas outlet.

2. The radial turbomachine as claimed in claim 1, wherein, in each case, the first housing part and the second housing part are produced as a whole in one piece.

3. The radial turbomachine as claimed in claim 1, wherein the gas outlet is an axial gas outlet.

4. The radial turbomachine as claimed in claim 1, wherein the second housing part or the first housing part comprises a deflection element which serves for deflecting the gas flowing out of the flow channel in a direction of the gas outlet.

5. The radial turbomachine as claimed in claim 4, wherein the deflection element is configured to effect a deflection of the flowing gas by 90°.

6. The radial turbomachine as claimed in claim 4, wherein the deflection element at least partially protrudes into the gas outlet.

7. The radial turbomachine as claimed in claim 1, wherein the first housing part and the second housing part are configured in each case in a substantially plate-shaped manner on an outer face in a region of the flow channel.

8. The radial turbomachine as claimed in claim 1, wherein a sealing element is present between the first housing part and the second housing part in order to circumferentially seal the flow channel to the outside.

9. The radial turbomachine as claimed in claim 8, wherein the sealing element is circumferentially arranged around the gas outlet.

10. The radial turbomachine as claimed in claim 1, wherein the first housing part is produced from a metal.

11. The radial turbomachine as claimed in claim 1, wherein the first housing part forms a compartment which is closable by a cover for accommodating an electronics unit.

12. The radial turbomachine as claimed in claim 1, additionally having a coupling piece in order to connect the gas outlet to the gas inlet of a further radial turbomachine.

13. The radial turbomachine as claimed in claim 1, wherein a space which is fully sealed to the outside, except for the gas inlet and the gas outlet, is delimited by the first housing part and by the second housing part, said space encompassing at least the flow channel.

14. The radial turbomachine as claimed in claim 2, wherein, in each case, the first housing part and the second housing part are produced as a cast element.

15. The radial turbomachine as claimed in claim 10, wherein the second housing part is produced from a metal.

16. The radial turbomachine as claimed in claim 13, wherein said space encompasses at least the flow channel and the motor chamber.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0045] Preferred embodiments of the invention are described hereinafter with reference to the drawings which are merely explanatory and are not to be interpreted as limiting. In the drawings:

[0046] FIG. 1 shows a perspective view of a preferred embodiment of a radial turbomachine according to the invention;

[0047] FIG. 2 shows a central cross-sectional view of the radial turbomachine of FIG. 1 along the axis of rotation, wherein the radial impeller is omitted for illustrative reasons;

[0048] FIG. 3 shows a first perspective view of the inner face of the first housing part of the radial turbomachine of FIG. 1;

[0049] FIG. 4 shows a second perspective view of the inner face of the first housing part of the radial turbomachine of FIG. 1;

[0050] FIG. 5 shows a plan view of the inner face of the first housing part of the radial turbomachine of FIG. 1;

[0051] FIG. 6 shows a perspective view of the outer face of the second housing part of the radial turbomachine of FIG. 1;

[0052] FIG. 7 shows a perspective view of the inner face of the second housing part of the radial turbomachine of FIG. 1;

[0053] FIG. 8 shows a plan view of the inner face of the second housing part of the radial turbomachine of FIG. 1;

[0054] FIG. 9 shows a perspective view of the radial impeller, the drive motor and the electronics unit of the radial turbomachine of FIG. 1;

[0055] FIG. 10 shows a perspective view of two radial turbomachines which are arranged so as to be connected in series one behind the other and which in each case are configured according to the embodiment shown in FIG. 1;

[0056] FIG. 11 shows a side view of the two radial turbomachines of FIG. 10 which are arranged so as to be connected in series one behind the other;

[0057] FIG. 12 shows a central cross-sectional view of a further preferred embodiment of a radial turbomachine according to the invention with two radial impellers; and

[0058] FIG. 13 shows a perspective view of the turbomachine of FIG. 12.

DESCRIPTION OF PREFERRED EMBODIMENTS

[0059] FIGS. 1 to 13 show preferred embodiments according to the invention of a radial turbomachine in different views. Elements which have identical or similar functions are provided in each case with the same reference numerals.

[0060] As is visible in FIG. 1, the radial turbomachine according to the embodiment shown has an exceptionally compact and robust construction overall. This is based, in particular, on the simple configuration of the housing consisting of substantially only two housing parts 1 and 2 and on the plate-shaped design of the two housing parts 1 and 2 in the region where they bear against one another and where the gas passes through the turbomachine.

[0061] Both the first housing part 1 and the second housing part 2 are produced as a whole in one piece as a cast element from metal.

[0062] The first housing part 1 is shown in FIGS. 3 to 5 and, as in particular may be easily identified in FIG. 2, forms a motor chamber 11 in which a drive motor 6 is accommodated. Since the motor chamber 11 is configured as a bag-like recess in the housing part 1 and is configured to be open toward the second housing part 2, the drive motor 6 may be easily inserted into the motor chamber 11 when the second housing part 2 is removed. Otherwise, the motor chamber 11, with the exception of the upper face closed by a cover 3, is circumferentially enclosed by the first housing part 1. By this enclosure of the motor chamber 11 by the first housing part 1 an optimal dissipation of heat from the motor chamber 11 is possible.

[0063] The drive motor 6 is preferably an AC electric motor, in which the rotor is advantageously arranged internally and the stator is advantageously arranged externally. Advantageously the drive motor 6 is designed for rotational speeds of up to 40,000 RPM. The drive motor 6 serves for driving a drive shaft 61 and thereby for driving a radial impeller 5 which is attached fixedly in terms of rotation to the front end of the drive shaft 61 (FIG. 9). The rotational movement carried out by the radial impeller 5 during operation of the radial turbomachine defines an axis of rotation R (FIG. 2).

[0064] Above the drive motor 6 the first housing part 1 is configured to be open per se, but closed by the aforementioned cover 3. The cover 3 is also produced as a whole in one piece and as a cast element from metal. For the releasable fastening of the cover 3 to the first housing part 1 screws are screwed through screw holes 31 of the cover 3 into threaded bores 18 correspondingly provided on the first housing part 1 (see FIG. 3). By means of these screw connections and the direct bearing of the cover 3 against the first housing part 1 an effective dissipation of heat from the motor chamber 11 is also possible via the cover 3.

[0065] A compartment 13 which serves for accommodating an electronics unit 7 is provided below the cover 3, i.e. between the cover 3 and the drive motor 6. The electronics unit 7 serves, in particular, for controlling and supplying energy to the drive motor 6 and has a printed circuit board 71 with electronic components 711 attached to the upper and lower face. Additionally a plug connector 72, which protrudes outwardly through a through-opening provided correspondingly in the cover 3, is attached to the printed circuit board 71. The plug connector 72 serves for connecting an external control and energy supply unit, not shown in the figures. By screwing off the cover 3 from the first housing part 1, the electronics unit 7 is easily accessible and if required easily repairable or replaceable. A sealing element, for example an O-ring, may be provided between the cover 3 and the first housing part 1, said sealing element, for example, being inserted in a groove provided on the first housing part 1 in order to seal the compartment 13 and the motor chamber 11 to the outside.

[0066] The first housing part 1 circumferentially around the compartment 13 has a sealing groove into which a sealing element 32, which in particular may be configured as an O-ring, is inserted. The sealing element 32 serves for sealing the first housing part 1 relative to the cover 3 in the region of the compartment 13. Advantageously a further sealing element, which is not shown in the figures, however, and which is preferably configured as an O-ring, is arranged between the plug connector 72 and the cover 3 in order to provide a seal of the compartment 13 on the circumference of the plug connector 72 toward the outside.

[0067] As is visible for example in FIG. 3, the first housing part 1 in its region enclosing the motor chamber 11 has cooling ribs 17 on the outer face, which serve for dissipating heat energy from the motor chamber 11.

[0068] In the region of the front end of the motor chamber 11, i.e. facing toward the second housing part 2, the first housing part 1 transitions perpendicularly, i.e. relative to the axis of rotation R radially outwardly, into a circumferential protruding region 19. The first housing part 1 is configured in this protruding region 19 to be substantially plate-shaped at least on its side facing to the rear, i.e. in the direction of the motor chamber 11. The protruding region 19 has an approximately square shape overall.

[0069] Below the region which encloses the motor chamber 11, a base 16 of the first housing part 1 extends from the protruding region 19 to the rear. The base 16 which is connected at the top to the region of the first housing part 1 enclosing the motor chamber 11 has screw holes 161 for fastening the radial turbomachine to a further component or to a support element.

[0070] On the front face which faces the second housing part 2, the first housing part 1 in the region of the projection 19 has a recess which together with a recess of the second housing part 2, described further below, forms a flow channel 8. The flow channel is arranged concentrically circumferentially relative to the axis of rotation R and has an inner radial region 81 which transitions radially outwardly into a circumferential outer peripheral region 82. In the radial region 81 the first housing part 1 is slightly recessed but of planar configuration. In the peripheral region 82 the first housing part 1 is configured to be recessed over the circumference in an annular manner, wherein the recess of the radial region 81 in the radial direction over the circumference transitions into the annular recess of the peripheral region 82. The peripheral region 82 of the flow channel 8 is in this case delimited in the cross-sectional view according to FIG. 2 by rounded delimiting surfaces of the first housing part 1.

[0071] The peripheral region 82 of the flow channel 8 widens continuously relative to its cross-sectional surface in the peripheral direction, as may be clearly identified for example in FIG. 5. In the region shown at the top in FIG. 5, the recess which is configured in the first housing part 1 and which forms the peripheral region 82 of the flow channel 8 transitions tangentially and with a further widening cross-sectional surface into a gas outlet 12. The gas outlet 12 is formed by a gas outlet pipe 121 which extends to the rear on the rear face of the first housing part 1 parallel to the axis of rotation R. The gas outlet pipe 121 which is formed entirely by the first housing part 1 delimits a gas outlet opening through which the gas flowing out of the flow channel 8 may be blown out of the radial turbomachine. On its inner face the gas outlet pipe 121 has an internal thread for connecting, for example, an air line or a coupling element.

[0072] In order to permit a transition which is continuous, and thus as far as possible without turbulence, from the flow channel 8 to the gas outlet pipe 121, the recess which forms on the front face of the first housing part 1 the peripheral region 82 of the flow channel 8 transitions continuously via a rounded surface into the gas outlet pipe 121. In other words, the recess is increasingly recessed toward the gas outlet 12. Therefore, a continuous opening is configured in the region of the gas outlet 12 in the first housing part 1. The gas outlet pipe 121 extends parallel to the axis of rotation R out of the protruding region 19 to the rear.

[0073] Over the circumference around the recess forming the flow channel 8, the first housing part 1 has a sealing groove 14 into which a sealing element 4 in the form of an O-ring is introduced. The sealing groove 14 and thus the sealing element 4 are not only arranged over the circumference around the flow channel 8 but also around the gas outlet 12 and/or around the through-opening formed by the gas outlet 12. The sealing element 4 serves for sealing the first housing part 1 relative to the second housing part 2 in the region of the flow channel 8.

[0074] In each case, threaded bores 15 which serve for fastening the second housing part 2 to the first housing part 1 are provided in the corners of the protruding region 19 of the first housing part 1.

[0075] The second housing part 2 is shown, in particular, in FIGS. 6 to 8. As may be identified in FIG. 6, the second housing part 2 has overall a substantially plate-shaped outer shape, with the exception of a gas inlet pipe 211 protruding on the front face and a deflection element 22 protruding on the rear face. The second housing part 2 in this case describes a substantially square shape, corresponding to the shape of the projection 19 of the first housing part.

[0076] The gas inlet pipe 211 is arranged concentrically to the axis of rotation R and extends outwardly parallel thereto from the front face, which is otherwise of substantially planar configuration, of the second housing part 2. A gas inlet opening extends continuously through the gas inlet pipe 211 and the second housing part 2 and thus forms a gas inlet 21. On its inner face the gas inlet pipe 211 has an internal thread 212 for connecting, for example, an air line or a coupling element.

[0077] On the rear and inner face of the second housing part 2, respectively, which may be identified in FIGS. 7 and 8, a recess is configured concentrically and circumferentially to the gas inlet 21, said recess jointly forming and delimiting the flow channel 8 with the recess described further above of the first housing part 1. Similar to the recess of the first housing part 1, that of the second housing part 2 also has an inner region which delimits the radial region 81 of the flow channel 8 as well as an outer region which delimits the peripheral region 82 of the flow channel 8.

[0078] The inner region of the recess of the second housing part 2 which forms the radial region 82 of the flow channel 8 has a conically configured front delimiting surface with an opening angle oriented toward the first housing part 1 along the axis of rotation R. The conical delimiting surface, which in particular is clearly identifiable in FIG. 2, corresponds to the similarly conically configured front face of the radial impeller 5.

[0079] In the radial direction an annular recess which forms the peripheral region 82 of the flow channel 8 circumferentially adjoins the conical delimiting surface. Similar to the annular recess of the first housing part 1, the annular recess of the second housing part 2 also continuously widens in the circumferential direction and has a rounded delimiting surface.

[0080] In the region shown at the top in FIG. 8, the recess which forms the peripheral region 82 of the flow channel 8 is guided further in the tangential rectilinear direction to a deflection element 22. When the first and the second housing part are connected together as intended, the deflection element 22 protrudes into the gas outlet 12 and, in particular, the gas outlet pipe 121 of the first housing part 1. The deflection element serves to deflect the gas flowing out of the flow channel 8, as far as possible without turbulence, by ca. 90° and to conduct the gas into the gas outlet pipe 121. To this end, the deflection element 22 has a continuously rounded inner surface along which the gas flow is deflected by ca. 90° in a direction extending parallel to the axis of rotation R. Moreover, the deflection element 22 also has in the cross section of the gas flow a rounded delimiting surface which continuously transitions into the rounded delimiting surface which is configured by the recess of the second housing part 2, which forms the peripheral region 82 of the flow channel 8.

[0081] Around the recess which forms the flow channel 8 the second housing part 2 has a sealing surface 23 which is configured to be planar as a whole. The sealing surface 23 extends both circumferentially around the gas inlet 21 and around the deflection element 22. The sealing surface serves for the bearing of the sealing element 4 and thus as a sealing seat for sealing the flow channel 8 to the outside.

[0082] In each case, screw holes 24 through which screws are able to be screwed into the threaded bores 15 of the first housing part 1 are provided in the corners of the second housing part 2 in order to fasten the second housing part 2 to the first housing part 2.

[0083] The flow channel 8 is thus formed, on the one hand, by a recess which is configured on the side of the first housing part 1 facing toward the second housing part 2 and, on the other hand, by a recess corresponding thereto, which is configured on the side of the second housing part 2 facing toward the first housing part 1. In the peripheral region 82 the flow channel 8 has continuously an approximately circular cross-sectional surface. An approximately circular cross-sectional surface is also present in the extension of the flow channel 8 in the region of the deflection element 22 and in the gas outlet pipe 121. Due to this continuously circular cross-sectional surface, a gas guidance is achieved inside the turbomachine which is substantially without turbulence.

[0084] The radial impeller 5 which is shown in FIG. 9 is attached in the region of a hub 52 fixedly in terms of rotation to the drive shaft 61. In the region of the hub 52 and thus concentrically to the axis of rotation R a circular inlet opening which forms an air inlet region 55 is configured in a front wall 53 of the radial impeller 5. Impeller blades 51 arranged between the front wall 53 and a rear wall 54 in each case extend approximately radially outwardly and serve during operation to convey radially outwardly the gas flowing into the air inlet region 55. The gas leaves the radial impeller 5 in this case via an air outlet region 56 arranged radially on the outside.

[0085] Due to the conical configuration of the front wall 53 the space for the gas in the radial direction to the outside reduces between the front wall 53 and the rear wall 54. The gas is thus increasingly compressed when conveyed to the outside.

[0086] The radial impeller 5 is arranged in the radial region 81 of the flow channel 8, i.e. between the first housing part 1 and the second housing part 2.

[0087] Due to the sealing elements 4 and 32, the internal space which is delimited by the first housing part 1, the second housing part 2 and the cover 3, and which comprises the flow channel 8, the motor chamber 11 and the compartment 13, with the exception of the gas inlet 21 and the gas outlet 121, is fully sealed to the outside and preferably according to IP 67 to IEC standard 60529. During the operation of the turbomachine, therefore, preferably a pressure prevails in the motor chamber 11 and in the compartment 13 which is raised relative to the external pressure and which, in particular, may substantially correspond to the pressure in the flow channel 8.

[0088] During operation of the radial turbomachine, the radial impeller 5 is set in rotational movement about the axis of rotation R by the drive motor 6. As a result, by means of the impeller blades 51 a gas and/or air is suctioned through the gas inlet pipe 211 into the flow channel 8 and conveyed in the radial region 81 thereof radially to the outside. The impeller blades 51 move the gas at the same time in the circumferential direction, said gas thus passing along a spiral from the radial region 81 into the peripheral region 82 of the flow channel 8. Via the peripheral region 82 the compressed gas passes to the deflection element 22 where it is deflected by ca. 90° in a direction extending parallel to the axis of rotation R and is blown out through the gas outlet pipe 121.

[0089] In order to increase further the pressure of the gas, a plurality of such radial turbomachines may be connected in series one behind the other. To this end, the gas outlet pipe 121 of a first radial turbomachine may be coupled to the gas inlet pipe 211 of a second radial turbomachine which is shown in FIGS. 10 and 11. The outlet pressure is doubled thereby or correspondingly multiplied when further such radial turbomachines are connected one behind the other.

[0090] For coupling the two radial turbomachines a coupling piece 9 may be used, said coupling piece being able to be screwed, on the one hand, into the internal thread of the gas outlet pipe 121 of the first radial turbomachine and, on the other hand, into the internal thread 212 of the gas inlet pipe 211 of the second radial turbomachine.

[0091] In the case of radial turbomachines which are arranged so as to be connected in series one behind the other, in order to achieve a relatively compact arrangement the two turbomachines may be mutually arranged so as to be rotated relative to one another by 180°, as shown in FIG. 10. The gas outlet 12 of the second radial turbomachine is thus exactly aligned with the gas inlet 21 of the first radial turbomachine.

[0092] As a further possibility for increasing the gas pressure a plurality of stages, with one respective radial impeller 5, may be provided inside the radial turbomachine. A corresponding embodiment is shown in FIGS. 12 and 13. The two radial impellers 5 are both attached fixedly in terms of rotation to the drive shaft 61 and thus are drivable by the drive motor 6. An intermediate part 10 is arranged between the first housing part 1 and the second housing part 2 in the region between the two radial impellers 5. The intermediate part 10 delimits the flow channel 8 on both sides, i.e. on the one hand toward the first housing part 1 and on the other hand toward the second housing part 2. The gas flowing in through the gas inlet pipe 211 of the second housing part 2 thus initially passes into a first radial region 81 of the flow channel 8 in the region of the first radial impeller 5, which forms a first (high pressure) stage of the turbomachine. From this first radial impeller 5 the gas then is conveyed radially outwardly into a first peripheral region 82 and from there along the rear face of the first radial impeller 5 again in the direction of the axis of rotation R and axially through a through-opening arranged centrally in the intermediate part 10. From this through-opening the gas passes directly into a second radial region 81 of the flow channel 8 which is located in the region of the second radial impeller 5. The second radial impeller 5 forms a second (low pressure) stage of the turbomachine. From the second radial impeller 5 the gas is conveyed radially outwardly into a second peripheral region 82 of the flow channel 5 and finally outwardly through the gas outlet pipe 121. For an optimal adaptation to the respective pressure conditions, the first and the second radial impeller 5 and also the first and second radial region 81 and the first and second peripheral region 82 are designed and, in particular, dimensioned differently in each case.

[0093] The preferably one-piece intermediate part 10 which is produced, in particular, as a cast element thus forms a further housing part of the radial turbomachine. The central through-opening provided in the intermediate part 10 in this case forms a gas inlet for the second (low pressure) stage and/or a gas outlet for the first (high pressure) stage of the turbomachine. Depending on the perspective, the first housing part 1 together with the intermediate part 10 or the second housing part 2 together with the intermediate part 10 may also be regarded as a multipart housing part 1, 10 and/or 2, 10.

[0094] Naturally, the invention described herein is not limited to the aforementioned embodiments and a plurality of modifications is possible. Thus in principle the gas outlet may also be formed by the second housing part 2 and delimited thereby over the circumference. The gas is then blown out from the gas outlet pipe in the opposing direction to that in which it is suctioned through the gas inlet pipe. The deflection element is then configured on the first housing part 1 rather than on the second housing part 2. Moreover, the radial impeller may also be designed in any other desired manner from the radial impeller 5 shown in FIG. 9. In particular, the front wall 53 or the rear wall 54 may also be dispensed with. Preferably, for reasons of stability, however, both the front wall 53 and the rear wall 54 are present. The coupling piece 9 may also be configured in any other desired manner and, for example, comprise a flexible connecting hose. A plurality of further modifications is conceivable.