Patent Application
20230193907
The invention relates to a side-channel machine.
Side-channel machines are known in general from the prior art. Side-channel machines are capable of conveying or compressing gas.
Generic side-channel machines are known, for example, from DE 103 34 950 A1, DE 197 08 953 A1, DE 103 34 812 A1, and DE 199 06 515 C1.
The invention addresses the problem of creating a very efficient and quiet side-channel machine. Furthermore, the side-channel machine should have a very high output density.
This problem is solved in accordance with an embodiment of the invention. Geometry optimization and targeted current guidance of the side-channel machine result in improvements in at least one of the performance parameters thereof. Advantageously, the output density, efficiency and/or noise generation of the side-channel machine is improved in comparison with conventional side-channel machines. The gas that is to be conveyed is preferably air or an industrial gas. The side-channel machine is preferably designed as a side-channel blower or side channel compressor. It is advantageous if the side-channel machine is capable of functioning in a vacuum and/or compressor mode.
The side-channel machine has a single- or multi-stage design.
The at least one gas intake opening and the at least one gas discharge opening are disposed at a spacing to one another about the rotational axis in the flow direction of the gas. It is advantageous if there is an angle about the rotational axis of at least 170° between them.
The impeller is effectively connected, directly or indirectly, to a motor or drive.
The at least one interrupter is preferably mounted on the housing, or is an integral component thereof.
The at least one gas intake pipe and/or the at least one gas discharge pipe are/is preferably mounted on the housing, or an integral component thereof.
When the side-channel machine is in operation, gas is conveyed about the rotational axis in the direction of flow from the at least one gas intake opening to the at least one gas discharge opening, which is disposed downstream of the at least one gas intake opening. The gas is thus conducted in the side channel in a substantially annular manner. It is preferably pushed radially outward in the side channel by centrifugal force, and subsequently conducted back to the radially inward region of the side channel with respect to the rotational axis, where it returns to impeller cells between adjacent impeller blades, and is again subjected to the centrifugal force.
It is advantageous when there are two conveniently adjacent gas intake openings and exactly one gas discharge opening, as well as exactly one interrupter. Alternatively, there may be more than two gas intake openings, and numerous gas discharge openings, and/or interrupters.
It is useful for the side channel to have two impeller flutes. By way of example, there is exactly one gas intake pipe, which is designed to distribute, in particular in a uniform manner, the gas onto the two impeller flutes. Alternatively, one gas intake pipe is dedicated to each impeller flute.
Further advantageous designs of the invention are specified in the dependent claims.
It is advantageous when the at least one gas discharge pipe adjoins the side channel in a substantially tangential manner, in order to discharge the gas from the side channel in a substantially tangential direction. Pressure losses can be reduced through the substantially tangential arrangement of the at least one gas discharge pipe on the side channel, resulting in an improvement in the efficiency of the side-channel machine. It is advantageous when the at least one gas discharge pipe adjoins the side channel at an absolute tangent thereto, such that the gas is discharged from the side channel in a tangential direction.
Ideally, the angle over the rotational axis between an upstream connection of the at least one gas discharge pipe on the side channel and a downstream outlet of this gas discharge pipe is between 280° And 320°, preferably between 290° and 310°. This design also results in a reduction in pressure losses.
It is advantageous when the side channel is delimited by a radially outer ceiling, with respect to the rotational axis, wherein the at least one gas discharge opening adjoins the ceiling without a transition, and is substantially tangential thereto. Eddy shedding on the impeller blades and the at least one gas discharge pipe can be reduced through this design, so that curve reductions or pressure losses can be avoided. Furthermore, this can also reduce operating noises generated by the side-channel machine. It is advantageous when the at least one gas discharge pipe adjoins a ceiling that delimits the side channel radially outward in an absolutely transitionless and tangential manner.
The side channel is preferably delimited by a base on the radial interior of the rotational axis, wherein the at least one gas discharge pipe adjoins the base substantially without transition, and in a substantially tangential direction. The explanations regarding the radially outer ceiling apply in a substantially analogous manner to another embodiment. It is advantageous when the at least one gas discharge pipe adjoins a base that delimits the side channel radially inward without a transition and tangentially.
It is useful when a flow cross section in the at least one gas discharge pipe expands, at least in part, in the flow direction of the gas, wherein opposing flow guidance walls of the at least one gas discharge pipe preferably assume an expansion angle of no more than 11°, preferably no more than 9° in relation to one another in at least one upstream starting region of the at least one gas discharge pipe.
It is advantageous when the at least one gas discharge pipe has at least one, preferably radial inner wall with respect to the rotational axis, which runs substantially parallel to an absolute speed vector of the gas flow in the side channel, adjacent at the downstream side to the at least one interrupter. Noises caused by the gas striking the at least one interrupter can be prevented with this side-channel machine, ensuring that the side-channel machine can be operated with a particularly low noise generation. The gas thus flows conveniently along the at least one wall of the at least one gas discharge pipe. It is advantageous when this at least one wall is present on the at least one interrupter. It is useful when the at least one wall runs absolutely parallel to an absolute speed vector of the gas flowing in the side channel adjacent to the at least one interrupter on the upstream side.
With the side-channel machine according to another embodiment, an interrupter-gas mass flow can be removed without damage into the at least one gas discharge pipe. The at least one outlet channel ideally has a circular cross section, and preferably runs in a radial direction with respect to the rotational axis. In particular, it is straight.
Another embodiment prevents gas from flowing unintentionally back from the at least one gas discharge pipe into the side channel or the at least one interrupter, which would have a negative impact on the efficiency and noise generation. It is advantageous when the at least one valve is disposed on the at least one interrupter, substantially on the discharge side with respect to the gas flow.
With another embodiment, the gas can be vacuumed off in a simple manner from at least one of the impeller cells adjacent to the at least one outlet channel.
It is advantageous when the cross section constriction necessary for forming the Venturi assembly is located in the at least one gas discharge pipe.
With another embodiment, the gas can be reliably vacuumed off in a simple manner from at least one of the impeller cells adjacent to the at least one outlet channel.
With another embodiment, the gas can be reliably vacuumed off in a simple manner from at least one of the impeller cells adjacent to the at least one outlet channel.
Impairments to the vacuuming of the gas in the at least one vacuum channel can be prevented through the spacing between the downstream intake opening of the at least one vacuum channel in the side channel and an upstream start of the at least one vacuum channel in another embodiment.
According to another embodiment, at least one relief groove is disposed in the at least one interrupter, starting from the side channel. The relief noise of the gas that is caused when the side channel is operating by the excited interrupter-gas mass flow escaping from the impeller cells can be reduced by the at least one relief groove. Furthermore, useable volume flows can be reduced by blocking an intake cross section.
Effects of the cell relief in the at least one gas intake pipe can be prevented through another embodiment, such that the useful vacuum volume flow remains unaffected.
Another embodiment effectively prevents the generation of noises and turbulences.
Pressure losses can be reduced through the substantially tangential arrangement of the at least one gas intake pipe on the side channel in accordance with another embodiment, resulting in an improvement in the efficiency of the side-channel machine. It is advantageous when the at least one gas intake pipe adjoins the side channel at an absolute tangent for a tangential introduction of the gas into the side channel.
Preferred embodiments of the invention shall be described below in an exemplary manner with reference to the attached drawings. Therein:
First, in reference to
The housing 4 comprises a first housing part 8 and a second housing part 9. The first housing part 8 and the second housing part 9 are joined as shown in
The impeller has a disk-like design. It comprises an inner impeller hub 11 with a central, circular hub bore 12. The impeller hub 11 is formed by an inner hub foot 13, which delimits the hub bore 12 radially toward the outside, and a radial, circular hub disk 14 adjoined thereto. Furthermore, the impeller 3 comprises a radial outer carrier ring 15, which adjoins the hub disk 18 on the outside, and overlaps it on both sides toward the longitudinal central axis 5. The carrier ring 15 has a number of impeller blades 2 distributed over its circumference, which extend radially away from the carrier ring 15. In particular, the impeller blades 2 are equidistant to one another. Impeller cells 50 are delimited by the impeller blades 2 in the direction of the circumference.
The drive shaft 10 is accommodated in the central hub bore 12. A conventional fitted key connection is provided between the drive shaft 10 and the hub foot 13 for transferring a torque applied by the drive shaft 10 to the impeller hub 11 in order to rotate the impeller 3.
The first housing part 8 has a central hub section 16, which radially and axially delimits a partial hub receiving space 17. A central shaft bore 18 passes through the hub section 16, opening into the partial hub receiving space 17. An annular side wall 19 adjoins the hub section 16, which extends radially outward from the hub section 16. A circumferential channel section 20 borders the outside of the side wall 19. The hub section 16, the side wall 19, and the channel section 20 are integrally formed as a molded unit, and form the first housing part 8.
The second housing part 9, which is screwed to the first housing part 8 with numerous fastener screws 21 also has a central hub section 22, which radially and axially delimits the partial hub receiving space 23. An annular side wall 24 adjoins the hub section 22, running radially outward.
A circumferential channel section 25 is connected to the outside of the side wall 24. A roller bearing 26 for the drive shaft 10 is disposed in the hub section 22. The hub section 22, the side wall 24 and the channel section 25 are integrally formed as a molded unit, and collectively form the second housing part 9.
The first housing part 8 and the second housing part 9 are connected to one another in the assembled state such that the two partial hub receiving spaces 17, 23 collectively delimit a hub receiving space 27, and the two channel sections 20, 25 collectively delimit a side channel 28 for conveying the gas. The two side walls 19, 24 are parallel to one another. The side channel 28 extends in an annular manner about the longitudinal central axis 5.
For practical purposes, the second housing part 9 forms a housing cover that can be removed from the first housing part 8. Alternatively, the reverse is also possible.
The side-channel blower 1 has two gas intake pipes 29. There is a gas intake pipe 29 on each housing part 8, 9. Each gas intake pipe 29 supplies a flute in the side channel 28. The gas that is to be conveyed in a flow direction 30 into the side-channel blower 1 can be introduced via the gas intake pipes 29 when the side-channel blower 1 is in operation.
Furthermore, the side-channel blower 1 has a gas discharge pipe (not shown), formed by the two housing parts 8, 9. There is a flow connection between the gas discharge pipe and the side channel 28. The gas can be removed from the side-channel blower 1 in a flow direction 32 via the gas discharge pipe. The gas intake pipes 29 and the gas discharge pipe are substantially perpendicular to one another.
The hub foot 13 of the impeller 3 is disposed in the hub receiving space 27 that is delimited by the hub sections 16, 22 when the side-channel blower 1 is assembled, wherein the drive shaft 10 passes through the hub bore 12. The hub disk 14 of the impeller 3 extends radially outward from the hub foot 13 between the spaced apart side walls 18, 24 of the housing 4. The carrier ring 15 and the impeller blades 2 are located in the circumferential side channel 28 thereby.
A first embodiment of the invention shall be explained below with reference to
The side channel 28 in the side-channel blower 1 is spatially delimited, radially inward by a base 35, and radially outward by a ceiling 36, with respect to the longitudinal central axis 5. The base 35 and the ceiling 36 are opposite one another and spaced apart, such that they delimit the side channel 28. They are formed on the housing 4a.
A gas discharge pipe 31a is connected to the side channel 28, substantially tangential thereto, in the side-channel blower 1a in accordance with
The gas discharge pipe 31a expands substantially evenly in the flow direction 32 of the gas.
As can also be derived from
Pressure losses in the side-channel blower 1a can be effectively reduced by the substantially tangential arrangement of the pipes 29a, 31a on the side channel 28.
An interrupter 39 is disposed in the side channel 28 between the gas discharge opening 33 and the at least one gas intake opening 34. The interrupter 39 has a side wall 40 adjacent to the gas discharge opening 33. Furthermore, the interrupter 39 has a radial inner wall 41, and a radial outer wall 42 opposite the inner wall 41, with respect to the longitudinal central axis 5.
A second embodiment of the invention shall be described below with reference to
With the side-channel blower 1b, the at least one gas intake pipe 29a again adjoins the side channel 28, substantially tangential thereto.
The gas discharge pipe 31b adjoins the side channel 28 at an absolute or full tangent. In accordance with
It is advantageous when the gas discharge pipe 31a expands downstream of the gas discharge opening 33. It is particularly preferred that an inner flow guidance wall 37 of the gas discharge pipe 31b adjoining the base 35 deviates by an angle b from the parallel to an opposite outer flow guidance wall 38 of the gas discharge pipe 31b, as is indicated by a broken line in
For practical purposes, there is a connection angle c, lying between 290° and 310° in relation to the longitudinal central axis 5, between a connection 55 of the gas discharge pipe 31b to the side channel 28 and the radially inner flow guidance wall 37 at the discharge of the side-channel blower 1b.
A third embodiment of the invention shall be described below in reference to
In the side-channel blower 1c depicted in
A vacuum channel 44 adjoins the outlet channel 43 on the downstream side, at the radial interior thereof, which opens into the side channel 28 at a spacing to the outlet channel 43. The point of entry, or entry opening 45 of the vacuum channel 44 in the side channel 28 is located basically opposite the outlet channel 43. The entry opening 45 is spaced apart from the outlet channel 43 at an angle d over the longitudinal central axis 5 lying between 120° and 140°. The vacuum channel 44 has a larger, in particular substantially larger, cross section area B than the outlet channel 43.
Gas is vacuumed via the outlet channel 43 out of an impeller cell 50 of the rotating impeller 3 that is currently adjacent to an intake opening of the outlet channel 43 opening into the side channel 28. The gas is conveyed, e.g. through pressure differences, in particular between the intake opening 56 and the entry opening 45. In particular, the pressure at the entry opening 45 is lower than at the intake opening 56. The impeller cells 50 are spatially delimited in the circumferential direction of the side channel 28 by adjacent impeller blades 2. The gas then flows into the vacuum channel 44 and re-enters the side channel 28 via the entry opening 45.
A fourth embodiment of the invention shall be described below with reference to
In the side-channel blower 1d depicted in
The inner wall 41 and the outer wall 42 form an angle e of preferably between 15° and 40°, more preferably between 20° and 30°.
The gas discharge pipe 31 can expand in the direction of flow 32.
A fifth embodiment of the invention shall be explained below with reference to
Structurally different but functionally identical parts are labeled with the same reference symbols, followed by an “e.”
In contrast to the embodiment depicted in
For a reliable vacuum, the following applies in particular: pU>pT, wherein pU is the pressure prevailing in the impeller cell 50 at the outlet channel 43e, and pT is the pressure prevailing downstream of the outlet channel 43e in the gas discharge pipe 31.
A removal of the gas via the outlet channel 43e from the side channel 28 to the gas discharge pipe 31 is particularly reliable when the following condition is also fulfilled:
V1: suction volume flow or vacuum volume flow in the outlet channel 43e
u: circumferential speed of the impeller
AK: cross section area of the side channel 28 on the pressure side
p2/p1: pressure ratio over the side-channel blower 1e
Di: diameter of the impeller at the base of the impeller blade
Da: outer diameter of the impeller
The suction volume flow is therefore dependent on the circumferential speed of the impeller, the cross section area of the side channel on the pressure side, the pressure ratio over the side-channel blower, and the diameter of the impeller at the base of the impeller blade, and the outer diameter of the impeller.
A dead space hollow 47 extends from the gas discharge pipe 31 or the outer wall 42e of the interrupter 39e in accordance with a preferred embodiment. The outlet channel 43e opens into the dead space hollow 47.
A self-actuating valve plate 49 is attached to the interrupter 39e in the dead space hollow 47 via at least one attachment means 48, which closes the outlet channel 43e at the downstream end region thereof with respect to its intake opening 56 when it is in its closed position. In the open position, the valve plate 49 is lifted at least in part away from the interrupter 39e, and thus at least partially opens the outlet channel 43e to the gas.
The gas discharge pipe 31 thus has an expanded cross section area in the region of the dead space hollow 47. A gas dead space region is formed in the dead space hollow 47 when the side-channel blower 1e is in operation. There is thus a reduced gas pressure in the dead space hollow 47, such that gas is suctioned out of the impeller cell 50 that is currently adjacent to the outlet channel 43e when the valve plate 49 is open. When it is closed, valve plate 49 prevents an unintentional backflow of the gas from the gas discharge pipe 31, or the dead space hollow 47, into the outlet channel 43e, or the side channel 28, respectively.
Alternatively, a design without a valve plate 49 is also possible. The valve plate 49 can also be present in the design depicted in
A removal of the gas via the outlet channel 43e from the side channel 28 to the gas discharge pipe 31 is particularly reliable when the following condition is fulfilled:
Av: cross section area of the vena contracta of the Venturi nozzle in the gas discharge pipe 31
The suction volume flow is thus dependent on the circumferential speed of the impeller, the cross section area of the side channel at the pressure side, the pressure ratio over the side-channel blower, the diameter of the impeller at the base of the impeller blade, and the outer diameter of the impeller, as well as the cross section area of the vena contracta of the Venturi nozzle in the gas discharge pipe.
A sixth embodiment of the invention shall be described below with reference to
Structurally different but functionally identical parts are labeled with the same reference symbols, followed by an “f.”
The side-channel blower if has a flow-reducing projection 51, instead of the dead space hollow 47 on the interrupter 39f, which extends into the gas discharge pipe 31. The outlet channel 43f also passes through flow-reducing projection 51. A valve plate 49 is preferably again attached to the flow-reducing projection 51 via at least one attachment means 48.
The gas discharge pipe 31 has a reduced flow cross section in the region of the flow reduction projection 51, such that the gas is conveyed there at a particularly high flow speed. Conversely, this results in a reduced pressure there, such that gas from the impeller cell 50 currently adjacent to the outlet channel 43f is vacuumed into the gas discharge pipe 31 via the outlet channel 43f. In this manner, a Venturi nozzle, or assembly, is basically created.
A seventh embodiment of the invention shall be described below with reference to
There is at least one relief groove 52 in the interrupter 39g, starting from the side channel 28. There is preferably a spacing x between an upstream starting point 53 of the relief groove 52 and an axial or circumferential impeller cell opening 54, which is at least 1.5 times the spacing r between adjacent impeller blades 2 over the longitudinal central axis 5. The radial depth t of the relief groove 52 increases gradually in relation to the longitudinal central axis in the direction of conveyance. The angle e of the relief groove 52 is advantageously in correlation with the pressure ratio p2/p1 and the circumferential speed u of the impeller, wherein p2 is the prevailing pressure in the impeller cells 50, and p1 is the vacuum pressure of the side-channel blower. When the impeller cells 50 are relieved, the circumferential speed of the impeller 3 and the flow speed overlap, such that translatory or even supersonic flows may also occur. An estimation of the occurrences of supersonic flows is obtained from the following equation:
Supersonic flows occur when M*u>M*ukrit. The at least one relief groove 52 can then be dimensioned according to the known laws of the “Prandtl-Meyer” function.
It is possible to combine the different embodiments, in particular with respect to the different pipes and interrupters.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102015213549.7 | Jul 2015 | DE | national |
This application is a continuation of U.S. patent application Ser. No. 17/011,604, filed on Sep. 3, 2020, which in turn is a continuation of U.S. patent application Ser. No. 15/743,296, filed on Jan. 10, 2018, which is a U.S. national stage entry of International Patent Application No. PCT/EP2016/066918, filed on Jul. 15, 2016, which claims priority to German Patent Application No. 10 2015 213 549.7, filed on Jul. 17, 2015, the entire contents of all of which are fully incorporated herein by reference.
| Number | Date | Country | |
|---|---|---|---|
| Parent | 17592033 | Feb 2022 | US |
| Child | 18084665 | US | |
| Parent | 17011604 | Sep 2020 | US |
| Child | 17592033 | US | |
| Parent | 15743296 | Jan 2018 | US |
| Child | 17011604 | US |
