EP1800010A2

EP1800010A2 - Side channel compressor and housing shells and rotor therefor

Info

Publication number: EP1800010A2
Application number: EP05795972A
Authority: EP
Inventors: Martin Baecke; Peter Hartung; Ingo Müller
Original assignee: Seleon GmbH
Current assignee: Seleon GmbH
Priority date: 2004-10-12
Filing date: 2005-10-05
Publication date: 2007-06-27
Anticipated expiration: 2025-10-05
Also published as: CN101076670B; ATE435373T1; WO2006039894A2; US20070231121A1; DE502005007633D1; ES2330768T3; WO2006039894A3; EP1800010B1; DE102004049613A1; US7591632B2; JP2008516128A; CN101076670A; JP5042840B2

Abstract

The invention relates to a side channel compressor, comprising a housing shell and a running wheel. The running wheel is mounted to be rotatable with respect to the housing shell to provide two annular sealing areas between the housing shell and the running wheel. The housing shell between the first and the second sealing area can be made of one piece. The gap dimensions of the first and second sealing areas can be adjusted by means of a disc spring/nut system or a wobble means. A fan impeller may be fixed on the motor shaft, and the housing shell can comprise cooling ribs, wherein the cooling ribs are arranged and formed such that the air conveyed by the fan impeller sweeps through the cooling ribs. One of the annular sealing areas can include a dead volume chamber. The housing shell may be a casting or a machined extruded profile.

Description

Side channel compressor as well as housing shells and impeller for this purpose

The field of the invention are compressors, in particular side channel compressors and impellers therefor.

Side channel blowers, housing shells and wheels according to the preambles 5 of the independent claims are known for example from WO 00/68577 A1.

In a side channel compressor, a housing and an impeller include a channel. On the impeller blades are mounted, which protrude into the channel, but not completely fill. Viewed in the direction of rotation of the impeller 0, an inlet to the channel is provided in front of an outlet from the channel. The channel comprises two areas, one traversed by the blades of the impeller, and the side channel which is not traversed by the blades. Between inlet and outlet a breaker is provided which closes the side channel. The effective length of the breaker must be slightly longer than a paddle distance. The interface between the side channel and the remainder of the channel is often a plane perpendicular to the axis of rotation of the impeller or a conical surface whose axis coincides with the axis of rotation of the impeller.

Through the inlet enters a fluid, often a gas, in particular air in the channel. Part of the fluid molecules is passed through a blade in the tangential direction

> o carried away. Due to the centrifugal force, the considered fluid molecules are also accelerated radially outwards and thus flow out of the blade into the side channel. There they are deflected in the direction of the impeller and learn through the impeller further acceleration. The fluid molecules are thus conveyed on a toroidally curved helical path from the inlet to the outlet, wherein

! 5 the pressure in the fluid increases. The breaker is intended to minimize the amount of fluid being drawn from the outlet to the inlet.

From DE 42 39 814 C2 a noise reduced side channel compressor is known. The noise reduction is achieved in that the inlet opening has a passage cross-section which is both smaller than the cross-section of the inlet opening and smaller than the cross-section of the side channel and the Transition between the different cross sections is continuous. FIG. 1 of this document shows a housing which has ribs on the outside.

DE 26 10 273 C3 deals with the optimization of the ratio of blade cell volume to the sum of blade volume plus blade cell volume. As a result, the amount of gas carried over the breaker is reduced, thus improving the efficiency.

DE 199 55 955 A1 also deals with an improvement in the efficiency of a side channel machine. The design changes only affect the blades.

WO 00/68577 A1 (= EP 1 177 384 A1), which claims the priority of DE 199 21 785 A1, likewise deals with the improvement of the efficiency of a side channel machine. For this purpose, a series of labyrinth seals are disclosed for sealing the gap between the impeller and the housing.

It is an object of the invention to provide a cost-effective side channel blower.

This object is achieved by the teaching of the independent claims.

Preferred embodiments of the invention are subject of the dependent claims.

A cost saving is achieved in particular by a structure in which the housing can consist of one piece, namely the housing shell, which houses the side channel.

A relative to the housing shell sealed lid, which can be made plan, reduces the leakage through the outer annular sealing point, protects the impeller from contact and the contact ends in front of the impeller

A cup-spring-nut system allows the adjustment of the two gap dimensions of the two annular sealing points, so that it is possible to work with higher tolerances during production and the gap losses nevertheless remain within the framework. This is especially true in the production of small ones Side channel compressors important, which must deliver a lower gas flow than the commercial side channel blower and of which one therefore expects a smaller design.

The direct attachment of the diaphragm spring-nut system to a motor shaft saves additional storage between the impeller and the housing shell.

The attachment of the engine z. B. by means of a swash plate on springs and screws on the housing shell allows against a diaphragm spring-nut system even more accurate adjustment of the gap.

The cooling of the side channel compressor can be improved in a simple manner by attaching a fan at the end of the motor shaft facing away from the impeller.

A honeycomb structure on the housing shell of the side channel compressor improves the rigidity of the shell and may additionally act as a cooling plate when the side channel compressor is mounted with the honeycomb structure upwards. In addition, the honeycomb structure for a given stiffness lowers the weight of the housing shell and the material consumption for the manufacture of the housing shell.

Intermediate vanes between the functional blades reduce noise without affecting the capacity of the side channel compressor.

In the following, a preferred embodiment of the invention will be explained in more detail with reference to the accompanying drawings. Showing:

1 shows a section through a side channel compressor with forced convection.

FIG. 2 is a perspective view of the forced convection side channel compressor shown in FIG. 1; FIG.

3 shows a channel with Totvolumenkammerabdichtung.

Fig. 4 is a plate spring-nut system for adjusting the axial clearance;

5 shows a second embodiment of a cup spring-nut system. 6 shows a third embodiment of a cup spring-nut system.

7 shows a section through a side channel compressor with wobble device;

FIG. 8 is a detail view of the tumbling device shown in FIG. 7; FIG.

9 shows a side channel compressor with a housing having a stabilizing honeycomb structure.

10 shows a side channel compressor with a housing which is made of an extruded cooling body. and

Fig. 11 is a paddle wheel with auxiliary blades.

Fig. 1 shows a section through a side channel compressor 1 according to the invention. The channel is located between the impeller 3 and the housing shell 2 in the region Y, which is shown enlarged in Fig. 3. The housing of a motor 4 may be attached directly to the housing shell 2. The impeller 3 is attached via a diaphragm spring-nut system in the region Z to the motor shaft. The area Z is shown enlarged in FIG. A cover 5 is fastened with screws 6 to the housing shell 2 and protects the rotating with more than 10'00 U / min impeller 3 against contact.

Cover 5 may be tight relative to the housing shell 2. This reduces the permeability of the outer sealing point 32. In the space between the impeller 3 and cover 5, a pressure is formed, which lies between the pressure at the inlet and the pressure at the outlet. If one assumes that the pressure at the inlet corresponds approximately to the ambient pressure, then cover 5 reduces the pressure difference at sealing point 32 shortly before the outlet, which reduces the leakage current accordingly.

In order for cover 5 to be as simple as possible a component which can be punched or cut, for example, from a sheet metal, housing shell 2 has an edge 10. Housing shell 2 is with the channel, the sealing points, the cooling fins and the inlet and outlet anyway a complicated component.

For heat dissipation housing shell 2 may be equipped with cooling fins 7. To further improve the heat dissipation, a fan 9 may be attached to the side facing away from the impeller 3 of the motor shaft. One Luftfügungsrohr 8 ensures that the promoted by fan 9 air sweeps as completely as possible by cooling fins 7. The Luftfügungsrohr 8 can be firmly clamped in notches 14 in the cooling fins 7, which allows easy assembly and disassembly of the air duct 8. In another embodiment, the Luftfügungsrohr 8 can also be stuck firmly.

Instead of the axial fan wheel 9 shown in FIG. 1, it is also possible to use a radial fan wheel. In a radial impeller, the vanes are typically arranged between two disks, one disk being driven and the other disk having a central hole through which air is drawn. The outer radius of the driven disc is smaller than the inner radius of the ventilation tube 8 by the distance between the two discs. The outer radius of the perforated disc is insubstantially smaller than the inner diameter of the ventilation tube 8 and the ventilation tube 8 is at least long enough to pierce the perforated disc Slice comes up and a narrow gap between the perforated disc and vent tube 8 remains. The radius of the perforated disc is not critical, but can be chosen so large that the area of the hole in the perforated disc is about as large as the clear surface between the driven disc and vent 8th

FIG. 2 shows a perspective view of the side channel compressor 1 shown in FIG. 1. Arrows indicate that cooling air is sucked in by fan 9, passed through ventilation tube 8 to the cooling fins 7 and then flows through the cooling fins 7 approximately radially outwards into the environment. In addition, FIG. 2 shows an inlet 11 and an outlet 12 for the air conveyed by impeller 3 and fastening eyes 13.

Fig. 3 shows the area Y enlarged. At the two sealing points 31 and 32 impeller 3 and housing shell 2 are particularly close. At the inner sealing point 31, a dead volume chamber seal 33 is provided by way of example. This has the goal to swirl the airflow flowing through the sealing gap between the impeller 3 and the housing shell 2 as much as possible and thus to make the flow resistance of the sealing gap as large as possible. If possible, there should be no current threads entering the next choke point. As the arrow in Fig. 3 indicates, the air in the channel rotates clockwise. In order to repel this circular air flow, the sealing gap runs at sealing point 31 from the channel to the bottom left before the sealing gap widens to Totvolumenkammer 33. In other words, the orientation of the seal is chosen so that the highest elevation is directed with respect to the direction of movement of the air molecules.

The Totvolumenkammer has an approximately circular cross-section, with a smaller circle segment of impeller 3 and a larger circle segment of housing shell 2 is cut. According to the course of the sealing gap, the leakage occurs from the top right in the dead volume chamber, flows through this and meets on the opposite side of the housing shell 2. This and the movement of the impeller 3 relative to the housing shell 2, the air is swirled, which the sealing effect of Totvolumenkammer promotes.

The Totvolumenkammerabdichtung 33 is shown only by way of example at the inner sealing points 31. It may alternatively or additionally be provided at the outer sealing points 32 substantially point-symmetrical to the center of the approximately circular channel cross-section.

Fig. 4 shows a first embodiment for the area Z increases. It recognizes impeller mount 41, which is glued to the motor shaft 40, for example, or fixed by means of a press fit. Disc spring 42 is clamped between a flange of the impeller mount 41 and impeller 3. On its other side impeller 3 is pressed by washer 44 and nut 43 against disc spring 42. By tightening or loosening of nut 43 against Laufradaufnahm e 41 plate spring 42 is pressed more or less together and the sealing gaps between impeller 3 and housing shell 2 reduced bew. Enlarged. The leadership of impeller 3 is mainly determined by the quality of the fit between the impeller 3 and impeller mount 41. Impeller mount 41 and impeller 3 can positively engage with each other. The positive connection can be generated by noses or flats

Fig. 5 shows a second embodiment for the region Z. In this embodiment, the washer is missing. In addition, a lock nut 46 is provided to unintentionally release nut 43 during operation prevent. The impeller 45 has a recess for nut 43 so that impeller 45 can serve as a wrench during assembly. This recess can be hexagonal to optimally transfer torque to nut 43. The recess may also be rectangular, wherein the short side of the rectangle corresponds to the nut width of the nut and wherein the effect of the recess is then more comparable to a fork wrench. More importantly, the positive connection between nut 43 and impeller 45, together with locknut 46, provides reliable torque transfer from motor shaft 40 to impeller 41 via impeller mount 41, thereby preventing slippage. Also in this embodiment, a fit between the impeller mount 41 and impeller 45 is provided.

6 shows the third embodiment for the region Z. In this embodiment, the central hole in impeller 48 has a fitting 50 in the lower region and a thread 49 in the upper region, which replaces nut 43. In another embodiment, thread 49 may extend over the entire central bore in impeller 48.

In order to simplify the setting of the sealing gaps, the end facing away from the impeller 3 of motor shaft 40, which protrudes beyond the motor housing or impeller 9, square, hexagonal, at least not be round.

Fig. 7 shows a section through a further embodiment of a side channel compressor according to the invention. In the side channel compressor shown in Fig. 7 fan 9 and Luftfügungsrohr 8 are not mounted. However, have cooling fins 7 notches 14, so that a ventilation tube 8 can be easily infected. Also, the motor shaft projects beyond the motor housing down, so that a fan 9 can be plugged. The interesting region X is shown enlarged in FIG.

Fig. 8 shows the attachment of the motor 4 by means of a swash plate 61 on the housing shell 2. Also in this embodiment impeller 3 is fixed by means of a Laufradaufnahme 64, a washer 65 and a nut 66 to the motor shaft 60. A plate spring is unnecessary, since the gap dimensions can be adjusted via adjusting screws 63, but can also be mounted. The motor housing is directly on swash plate 61, for example by means of Adhesive or screws attached. Springs 62 press swash plate 61 against adjusting screws 63 and thus suppress play. Swash plate 61, springs 62 and adjusting screws 63 may be referred to as a wobble device.

In another embodiment, not shown, swash plate 61 may be missing. The heads of the adjusting screws 63 rest in stepped holes in

Housing shell 2. The motor housing has threaded holes for the

Set screws on. Springs 62 push motor housing and housing shell 2 apart against the adjusting screws 63 to provide tension and

Suppress game. To simplify the setting process, impeller 3 has through holes above the adjusting screws through which the heads of the

Adjustment screws are accessible.

FIG. 9 is a perspective view of the side channel compressor shown in FIG. 7. FIG. In particular, the honeycomb structure 71 is shown, which gives the housing shell additional strength and leads to a material saving for a given strength. If honeycomb structure 71 is oriented upwards, as is the case in FIG. 9, so that heated air can rise, the honeycomb structure supports the effect of cooling fins 7.

In Fig. 10, another embodiment of a side channel compressor is shown, in which the housing shell 81 is made of an extruded profile.

Fig. 11 shows an impeller 93 with functional blades 94 and intermediate blades 95. In the installed state of impeller 93, the functional blades 94 range from a sealing gap to the breaker zoom. The intermediate blades 95 have a considerable distance to the breaker when installed. In one embodiment, its height is 2/3 of the height of the functional blades. The intermediate blades serve to reduce noise.

In a further embodiment, in particular the outlet-side edge of the breaker is arranged obliquely opposite to the blades of the impeller. This also serves to reduce noise. It is particularly advantageous if the angle between this edge and the blades of the impeller is selected so that this edge the space between the leading edges of two adjacent blades sweeps. The outlet side boundary of the breaker may also be composed of several edges. In the case of two edges this boundary has an arrow shape, in the case of more edges this border is saw-shaped with a multitude of saw teeth. The particularly advantageous length of a blade distance of the edges in the tangential direction is maintained.

The inlet-side edge of the breaker may be oblique just like the outlet-side edge and composed of several edges. Again, the preferred length in the tangential direction is a blade distance.

Although it has been assumed above that the side channel blower according to the invention is used primarily for the delivery of air, other gases or even fluids in general can be promoted. Due to the low compressibility of liquids, one does not have the problem here that the liquid dragged across the breaker expands in the area of the inlet.

The invention has been explained in detail above with reference to preferred embodiments. However, it will be apparent to those skilled in the art that various modifications and changes can be made without departing from the spirit of the invention. Therefore, the scope of protection is defined by the following claims and their equivalents.

O _O List of Reference Signs

1 side channel blower 45 impeller

2 housing shell 46 lock nut

3 impeller 25 47 paragraph

5 4 Motor 48 Impeller

5 cover 49 thread

6 screw 50 fit

7 Cooling fin 52 Housing shell

Air joining pipe 30 60 Motor shaft

10 θ Fan wheel 61 Swashplate

10 edge 62 spring

11 Inlet 63 Adjusting screw

12 outlet 64 impeller intake

13 Fixing lugs 35 65 Washer

15 14 notch 66 mother

31, 32 Sealing point 71 Honeycomb structure

33 Dead volume chamber seal 81 Housing shell

40 Motor shaft 93 Impeller

41 Impeller holder 40 94 Functional scoop

20 42 Disc spring 95 Intermediate bucket

43 nut Z, Y, X areas

44 washer

Claims

claims

1. Side channel compressor with:

a housing shell (2);

an impeller (3, 45, 48) which is rotatably mounted relative to the housing shell (2) such that it can be moved between the housing shell (2) and the impeller (3, 45,

48) are two annular sealing points (31, 32),

characterized in that the housing shell (2) between the first and second sealing point (31, 32) is made of one piece and the housing shell is sealed by a lid (5) with low height to the environment, wherein the impeller (3, 45, 48) is located substantially in the housing shell.

2. Side channel compressor according to claim 1, characterized in that the gap dimensions of the first and second sealing points (31, 32) by means of a diaphragm spring-nut system (42, 43) can be adjusted.

3. Side channel blower with:

a housing shell (2);

an impeller (3, 45, 48) which is rotatably mounted relative to the housing shell (2) such that there are two annular sealing points (31, 32) between the housing shell (2) and the impeller (3, 45, 48),

characterized in that the gap dimensions of the first and second

Seal points (31, 32) by means of a diaphragm spring-nut system (42, 43) can be adjusted.

4. Side channel compressor according to claim 1 or 3, characterized in that the impeller (3, 45, 48) by means of a plate spring (42) and a nut (43) on an impeller receptacle (41) is fixed, wherein the impeller receiving (41) a Having thread for screwing the nut (43), wherein the plate spring (42) between a flange of the impeller receiving (41) and the impeller (3, 45, 48) is clamped, so that the plate spring (42) the impeller (3, 45 , 48) against the nut (43) presses, wherein the impeller (3, 45, 48) by tightening or loosening the nut (43) axially against the impeller seat (41) can be moved.

5. Side channel compressor according to claim 4, characterized in that the impeller (45) has a shoulder (47) having a positive connection with the nut

(43) and a lock nut (46) against the nut (43) is tightened and so that a torque transmission from the impeller receiving (41) on the nut (43) is ensured.

6. Side channel compressor according to claim 1 or 3, characterized in that the impeller (48) by means of a lock nut (46) on a

Impeller (41) is fixed, wherein the impeller has a thread (49), wherein the impeller receiving (41) has a thread for screwing the impeller (48) and the lock nut (43), wherein the lock nut (46) against the nut (46). 43) is tightened and so a torque transmission from the impeller mount (41) on the impeller (48) is ensured.

7. Side channel compressor according to one of claims 2 to 5, characterized in that the plate spring-nut system (42, 43) on the shaft (40) of a motor (4) is fixed, wherein the housing of the motor (4) on the Housing shell (2) is attached.

8. Side channel compressor according to one of claims 1 to 6, characterized by a motor (4) on whose shaft (60) the impeller (3, 45, 48) is fixed, wherein the housing of the motor (4) by means of screws (63) and springs (62) are fixed to the housing shell (2) so that by turning the screws (63) the springs (62) are more or less compressed and the position and orientation of the motor (4) and the impeller (3, 45 , 48) relative to the housing shell (2) by the Eindrehiefe the screws (63) is fixed.

9. Side channel compressor with:

a housing shell (2); an impeller (3, 45, 48) which is rotatably mounted relative to the housing shell (2) such that there are two annular sealing points (31, 32) between the housing shell (2) and the impeller (3, 45, 48),

characterized by a motor (4) on whose shaft (60) the impeller (3,

5 45, 48) is fixed, wherein the housing of the motor (4) by means of screws (63) and springs (62) on the housing shell (2) is fixed so that by turning the screws (63), the springs (62) more or less and the position and orientation of the motor (4) and the impeller (3,

45, 48) relative to the housing shell (2) by the Eindrehtiefe the

10 screws (63) is fixed.

10. Side channel compressor according to claim 8 or 9, characterized in that the housing of the motor (4) is fixedly connected to a swash plate (61) which in turn by means of the screws (63) and the springs (62) with the housing shell (2). connected is.

15 11. Side channel compressor according to one of claims 7 to 10, characterized in that on the said impeller (3, 45, 48) facing away from the end of the motor shaft (40, 60) a fan (9) is fixed and the housing shell (2) cooling fins (7), wherein the cooling ribs (7) are mounted and shaped such that the air conveyed by the fan wheel (9) through the cooling ribs (7)

20 strokes.

12. Side channel compressor according to one of the above claims, characterized in that the housing shell (2) has on its outer side a honeycomb structure (41).

13. Housing shell (2) for a side channel compressor (1), characterized 25 characterized in that the housing shell (2) on its outer side a

Honeycomb structure (41).

14. Side channel compressor with a housing shell (2) according to claim 13, characterized by an impeller (3, 45, 48) which is rotatably mounted relative to the housing shell (2) so that it between the housing shell (2) and the impeller ( 3, 45, 48) two annular sealing points

(31, 32),

15. Side channel compressor according to one of claims 1 to 12 and 14, characterized in that at least one of the annular sealing points (31, 32) has a dead volume chamber (33).

16. Side channel compressor with:

a housing shell (2);

characterized in that at least one of the annular sealing points (31, 32) has a dead volume chamber (33).

17, side channel compressor according to one of claims 1-12 or 14-16, characterized in that the housing shell (2) is a casting or a machined extruded profile.

18. Housing shell (2) for a side channel compressor characterized in that the housing shell (2) is a casting or a machined

Extruded profile and the housing shell (2) has an edge (10) surrounding a round trough, which is so deep that the trough can accommodate a provided for the side channel compressor impeller (3, 45, 48).

19. Side channel compressor with a housing shell (2) according to claim 18, characterized by an impeller (3, 45, 48) which is opposite to the

Housing shell (2) is rotatably mounted so that there are two annular sealing points (31, 32) between the housing shell (2) and the impeller (3, 45, 48).

20. Side channel compressor according to one of claims 1 to 12, 14 to 17 and 19, characterized in that the impeller (3, 45, 48) two types of

Blades, namely functional blades (94) and intermediate blades (95).

21. An impeller for a side channel compressor, characterized in that the impeller (3, 45, 48) has two types of blades, namely functional blades (94). and intermediate blades (95), wherein the functional blades are slightly higher than the intermediate blades, wherein the height of the functional blades is dimensioned so that the functional blades extend from a sealing gap to the breaker of the side channel compressor when the impeller is installed in a side channel compressor, wherein the height of the intermediate blades is sized to leave a significant gap between the intermediate blades and the side channel compressor interrupter when the impeller is installed in a side channel compressor.