DE102013217261A1 - compressor - Google Patents

Abstract

The invention relates to a compressor for a heat pump cycle and / or refrigeration system, comprising a housing and a rotor rotatably mounted about a rotation axis, wherein the housing is at least partially circumferentially disposed of the rotor, wherein the rotor at least one hub and at least one radially outwardly on the hub arranged vane, wherein the vane is adapted to promote a main fluid flow, wherein the rotor comprises a radially outer side of the blade disposed shroud, wherein the shroud is radially spaced from the housing, wherein radially outside of the shroud a bearing structure is provided which is designed to form a bearing fluid flow between the shroud and the housing to form a fluid dynamic bearing for supporting the rotor in the housing.

Description

The invention relates to a compressor for a heat pump cycle and / or refrigeration system, comprising a housing and a rotor rotatably mounted about a rotation axis, wherein the housing is at least partially circumferentially disposed of the rotor, wherein the rotor at least one hub and at least one radially outwardly on the hub arranged vane, wherein the vane is adapted to convey a main fluid flow, wherein the rotor comprises a radially outwardly disposed on the blade shroud, wherein the shroud is radially spaced from the housing, wherein radially on the outside of the shroud a bearing structure is provided which is designed to form a bearing fluid flow between the shroud and the housing to form a fluid dynamic bearing for supporting the rotor in the housing.

State of the art

Compressors for heat pump circuits and / or refrigeration system circuits have a rotor which is rotatably mounted by means of rolling or plain bearings and is driven by a drive unit. The compressors are designed to pressurize a fluid from an input side to an output side and thus to compress the fluid.

It is an object of the invention to provide an improved compressor, which has a particularly good storage and at the same time is particularly inexpensive to produce.

Disclosure of the invention

This object is achieved by means of the features of patent claim 1. Advantageous embodiments are given in the dependent claims.

According to the invention, it has been recognized that an improved compressor can be provided in that the compressor comprises a housing and a rotor rotatably mounted about an axis of rotation. The housing is at least partially arranged circumferentially of the rotor. The rotor has at least one hub and at least one blade arranged radially on the outside of the hub. The vane is configured to convey a main fluid stream. The rotor has radially on the outer side on the blade a shroud arranged radially on the outside of the blade. The shroud is disposed radially spaced from the housing. Radially on the outside of the shroud a bearing structure is provided, which is designed to form a bearing fluid flow between the shroud and the housing to form a fluid dynamic bearing for supporting the rotor in the housing.

This embodiment has the advantage that a fluid-dynamic bearing of the rotor can be provided in the housing and thus can be dispensed with conventional sliding and rolling bearings. As a result, a particularly quiet mounting of the rotor can be provided, which is both particularly cost-effective and at the same time has a particularly long service life.

In a further embodiment, the rotor has an input side and an output side. The vanes are configured to convey the main fluid flow from the inlet side to the outlet side. The bearing structure is designed to promote the fluid flow from the outlet side to the inlet side. In this way, it can be ensured that at a pressure increase between the input side and the output side in the main fluid flow of the latter suspends the bearing fluid flow and so a reliable fluid dynamic bearing of the rotor is ensured. Furthermore, a particularly reliable storage can be ensured even at low speeds of the rotor.

In a further embodiment, the input side is arranged radially on the inside and the output side on the outside radially on the rotor, wherein the bearing structure is at least partially helical. This embodiment has the advantage that a particularly steady bearing fluid flow, which is both rotated in the circumferential direction and also conveyed in the axial direction in the direction of the inlet, can be provided.

In a further embodiment, the bearing structure comprises a sealing element, wherein the sealing element between the shroud and the housing is arranged, wherein the sealing element is designed to limit the bearing fluid flow in the axial direction. In this way it can be ensured that the compressor has a particularly high efficiency and the bearing fluid flow does not unnecessarily reduce the delivery volume of the compressor.

It is particularly advantageous if the sealing element is designed as a labyrinth seal.

In a further embodiment, the bearing structure is designed like a fishbone and / or wherein the bearing structure has a surface roughness (for example according to FIG EN ISO 25178 , previously called roughness) in the range from 1 Rz to 60 Rz. As a result, the bearing structure can be formed cost-effectively flat.

In a further embodiment, the bearing structure has at least one recess and / or a bulge, which is arranged obliquely or transversely to the circumferential direction of the hub. In this way, a particularly high peripheral speed of the bearing fluid flow can be achieved. As a result, a particularly stable mounting of the rotor in the housing can be ensured.

In a further embodiment, the rotor has a further hub, wherein on the further hub at least one radially outer side arranged further blade is provided. The further blade is designed to convey a further main fluid flow. The other hub is coupled to the hub via a shaft. The rotor comprises a further shroud arranged radially on the outside of the further blade. The further shroud is arranged radially spaced from the housing. The housing partially surrounds the further shroud, at least peripherally. Radially on the outside of the outer shroud another bearing structure is provided, which is designed to provide a further flow of bearing fluid between the further shroud and the housing. This embodiment has the advantage that the rotor is defined axially defined by the two oppositely arranged structures in its position, without the need for additional storage structures are provided.

It is particularly advantageous if the further bearing structure and the bearing structure are formed axially symmetrical to an axis of symmetry disposed between the two hubs. This can be avoided that different axial bearing forces are generated by the bearing structure and the other bearing structure, which would lead to a non-uniform orientation of the rotor in the compressor.

In a further embodiment, at least one magnet is arranged on the shaft between the two hubs, the magnet being connected in a torque-locking manner to the shaft. Radially on the outside of the shaft, at least one coil ring is provided for providing an alternating magnetic field, wherein the alternating magnetic field is designed to come into operative connection with the magnet in order to generate a rotational movement of the rotor. This allows the rotor to be driven particularly easily.

The invention will be explained in more detail with reference to figures. Showing:

1 a schematic sectional view through a compressor according to a first embodiment;

2 a section of the in the 1 shown sectional view;

3 a sectional view through the in the 1 to 2 shown compressor along a in 1 shown section plane AA;

4 a schematic sectional view through a compressor according to a second embodiment; and

5 a schematic sectional view through a compressor according to a third embodiment.

1 shows a sectional view through a compressor 10 according to a first embodiment and 2 shows a section of the in the 1 shown sectional view. 3 shows a sectional view through the in the 1 to 2 shown compressor 10 along an in 1 shown section plane AA. The compressor 10 includes a rotor 15 and a housing 20 , The housing 20 includes a first housing part 25 that in the 1 and 2 is arranged on the left side. Furthermore, the housing comprises 20 a right side in 1 arranged second housing part 30 , The rotor 15 is with a drive unit 35 coupled. The rotor 15 includes a wave 40 that with the drive unit 35 connected is. The wave 40 is rotatable about a rotation axis 45 ,

The compressor 10 has an entry page 50 and an exit side 55 on. The entrance page 50 is formed in the embodiment of a single channel, wherein the input side 50 then in two inlet channels 51 branched. Thus, the two inlet channels 51 connected in parallel with respect to their flow. Of course, it is also conceivable that the compressor 10 several different entrance pages 50 with correspondingly separate inlet channels 51 having. So can the inlet channels 51 in terms of their flow, for example, be connected in series, the output side 55 a first rotor section 110 in the entrance page 50 a second rotor section 115 empties. The rotor 15 is designed to be a fluid 60 from the entrance side 50 to the exit side 55 to promote and thereby increase an input side prevailing pressure p ₁ to a pressure p ₂ prevailing on the output side. The fluid 60 may be a refrigerant, for example CO ₂ , R-134a or R-410A. Of course, other fluids are conceivable. It is essential, however, that the fluid 60 is present in its gaseous phase state or its liquid phase state. The compressor 10 is intended as a turbocompressor for a refrigeration system circuit and / or heat pump cycle. Of course, another purpose is conceivable. So it is conceivable that compressor 10 to be used in a heating circuit with a solar collector and by means of the compressor 10 to promote the existing fluid in the heating circuit.

The rotor 15 has left side of the drive unit 35 a first rotor section 110 and a right side of the drive unit 35 arranged second rotor section 115 on. The first rotor section has a first hub 65 , first shovels 70 and a first shroud 75 on. The first shovels 70 are radially on the outside of the first hub 65 arranged and extend from radially inward to radially outward. The first shovels 70 are in the circumferential direction at a uniform distance from each other at the first hub 65 arranged. Radial on the outside connects to the first blades 70 the first shroud 75 at. The first shroud 75 is spaced radially outside to the first housing part 25 arranged. The first housing part 25 surrounds circumferentially the first shroud 75 and is on a shroud 75 facing inner first housing surface 76 corresponding to an outer circumferential surface 77 of the first cover band 75 educated. Due to the spaced arrangement is between the first housing part 25 and the first shroud 75 a first gap 80 provided with a gap width s ₁ . The first shroud 75 and the first hub 65 limit a first conveyor channel 85 , Due to the conical design of the first hub 65 and the likewise cone-shaped first shroud 75 runs the first conveyor channel 85 in the axial direction from the input side 50 towards the drive unit 35 radially from the inside to the outside and has a radially outwardly tapering cross-section.

The first shovels 70 are formed, the fluid 60 suck radially inward and in the axial direction in the direction of the output side 55 or the drive unit 35 to promote in the enterprise. To further increase the pressure, the rotor is 15 designed as a radial compressor and promotes the fluid 60 radially from the inside out, the pressure p from the input side 50 to the exit side 55 increases. To an imbalance of the rotor 15 To avoid are also the first hub 65 and the first shroud 75 rotationally symmetric to the axis of rotation 45 educated. The first shovels 70 are also evenly spaced in the circumferential direction on the first hub 65 arranged.

The rotor 15 has a second hub 90 , second shovels 95 and a second shroud 100 on. The second hub 90 is on the right side opposite to the left side hub 65 arranged. Radially outside are at the second hub 90 the second blades 95 intended. Radial on the outside of the second hub 90 opposite end of the blades 95 is the second shroud 100 with the second blades 95 connected. The second shroud 100 is over a second gap 105 spaced from the second housing part 30 arranged with a gap width s ₂ . An inner second housing surface 108 that is an outer peripheral surface 107 of the second shroud 100 facing, is corresponding to the outer peripheral surface 107 of the second shroud 100 educated. The second hub 90 is the same as the second shroud 100 cone-shaped. The second shroud 100 and the second hub 90 limit a second delivery channel 106 , The second conveyor channel 106 is in the axial direction from the input side 50 towards the drive unit 35 radially guided from inside to radially outside. Also the second conveyor channel 106 is from the input side 50 to the exit side 55 formed rejuvenating. Of course, it is also conceivable that the delivery channels 85 . 106 also have a constant or broadening cross-section. To an imbalance of the rotor 15 to avoid are also the second hub 90 and the second shroud 100 rotationally symmetric to the axis of rotation 45 educated. The second blades 95 are also equally spaced in the circumferential direction on the second hub 90 arranged. The second blades 95 serve as well as the first blades 70 to that, the fluid 60 from the entrance side 50 to the exit side 55 through the second conveyor channel 106 while promoting the fluid 60 to apply pressure p.

In the embodiment, the left side of the drive unit 35 arranged rotor section 110 axisymmetric to the right side of the drive unit arranged second rotor section 115 to one between the two rotor sections 110 . 115 arranged symmetry axis 120 educated. In each case a rotor section 110 . 115 is with an associated inlet channel 51 the input side 50 connected.

Of course, an asymmetric design of the rotor is also 15 conceivable. Indicates the compressor 10 several entrance pages 50 on, for example, each rotor section 110 . 115 one input page each 50 be assigned. By an asymmetrical design of the rotor 15 can the rotor 15 on the different entrance pages 50 be adjusted.

The drive unit 35 has at least one magnet 125 on, between the two rotor sections 110 . 115 is arranged and with the shaft 40 is connected torque-locking. Furthermore, the drive unit comprises 35 a coil wreath 130 with several coils 155 , the circumference the shaft 40 in the field of magnets 125 embraces. The coil wreath 130 is about a connection 135 with a control unit 140 connected. The control unit 140 is about another connection 145 with an energy source 150 connected. The control unit 140 is trained in the spool 130 arranged coils 155 to energize such that an alternating magnetic field through the coil ring 130 is provided, which is in operative connection with the magnets 125 occurs and a rotation of the shaft 40 causes the rotor 15 to put in a rotary motion.

The rotor rotates 15 around the axis of rotation 45 , so will through the first blades 70 a first main fluid stream 160 from the entrance side 50 to the exit side 55 over the first conveyor channel 85 promoted. The first main fluid flow 160 is due to the design of the first blades 70 guided radially from the inside to the outside and thereby subjected to pressure p ₂ . The pressure p ₂ on the output side 55 is thus higher than on the input side 50 ,

In the second rotor section 115 the promotion is analogous to the first rotor section 110 , In the second rotor section 115 is by means of the second blades 95 a second main fluid stream 161 in the axial direction of the drive unit 35 and radially fed from the inside to the outside and pressurized.

Due to the pressure difference between the output side 55 and the input side 50 that flows in the exit side 55 compressed fluid 60 in the first and second gap 80 . 105 as first or second bearing fluid flow 165 . 166 between the shrouds 75 . 100 and the housing parts 25 . 30 one. The gap width s ₁ , s ₂ is chosen such that between the housing part 25 . 30 and the shroud 75 . 100 the bearing fluid flow 165 . 166 less than the main fluid flow 160 . 161 , The flow direction of the bearing fluid flow 165 . 166 is from the exit side 55 in the direction of the entrance side 50 ,

The circumference is on the shroud 75 . 100 on one to the housing part 25 . 30 facing outer peripheral surface of a bearing structure 170 . 175 intended. The storage structure 170 . 175 accelerates into the gap 80 . 105 incoming bearing fluid stream 165 . 166 in the direction of rotation of the rotor 15 , This forms a fluid film 176 between the housing part 25 . 30 and the shroud 75 . 100 out. The storage structure 170 . 175 can be designed differently, to the bearing fluid flow 165 . 166 to accelerate in the circumferential direction. So can the storage structure 170 . 175 be designed as a surface roughness. In the 1 to 3 The acceleration is determined by the surface roughness of the shroud 75 . 100 generated. Depending on the speed, a surface roughness in the range of 1 Rz to 60 Rz is sufficient. Alternatively, it is also conceivable that the bearing structure 170 . 175 Bulges (cf. 5 ) and / or recesses (cf. 4 ), which are formed, the bearing fluid flow 165 . 166 to promote in the circumferential direction. Thus, the bearing fluid stream 165 . 166 both a velocity component in the axial direction and in the circumferential direction, wherein the velocity component in the circumferential direction predominates.

Will the bearing fluid flow 165 in the circumferential direction to a predefined speed by rotation of the rotor 15 brought, builds on the first / second shroud 75 . 100 a pressure pad 185 of the fluid film 176 or the bearing fluid stream 165 . 166 with a bearing force P ₁ , P ₂ . The curved design of the shroud 75 . 100 and the housing 20 As a result, the bearing force P ₁ , P ₂ obliquely to individual axes of a coordinate system 190 runs. The coordinate system 190 is exemplified as a rectangular coordinate system and should be used to facilitate directional designation of the forces. Thus, the bearing force P ₁ , P _{2 has} a bearing force P _x1 , P _x2 extending in the axial direction x and one perpendicular to the axis of rotation 45 and to the x-axis extending bearing force P _y1 , P _y2 . The bearing forces P _y1 , P _y2 in the y direction are counter to a weight F of the rotor 15 aligned. Are the bearing forces P _y1 , P _y2 in the y direction and the pressure pad 185 strong enough, the rotor lifts 15 off and is exclusively on the pressure pad 185 carried. Thus, the bearing fluid stream forms 165 . 166 a fluid dynamic fluid bearing 180 between the first shroud 75 and the first housing part 25 and the second shroud 100 and the second housing part 30 out, through which the rotor 15 contactless in the housing 20 can be stored. This takes place in particular when the gap width s ₁ , s _{2 of} the gap 80 . 105 at every point of the gap 80 . 105 in the range of 1 to 30 microns, preferably between 1 to 20 microns in the operation of the compressor 10 lies.

By the weight of the rotor 15 or by other influences is the axis of rotation 45 for example in the direction of the weight F offset to a housing axis 195 arranged. The housing axis 195 runs on the x-axis of the coordinate system 190 , By the offset of the rotor 15 is the gap width s ₁ , s ₂ in the circumferential direction in the operation of the compressor 10 different, wherein the underside, the gap width s ₁ , s _{2 is} less than the upper side of the rotor 15 ,

During startup or acceleration of the rotor 15 At operating speed, so if the bearing forces P _y1 , P _y2 in the y-direction together are smaller than the weight F, the bearing structure is 170 . 175 on the underside of the housing part 25 . 30 at. During startup forms the bearing structure 170 . 175 together with the housing parts 25 . 30 each a plain bearing to the rotor 15 in the case 20 to store.

Due to the symmetrical design of the shrouds 75 . 100 , and the associated one housing parts 25 . 30 as well as due to adjusting gap widths s ₁ and s ₂ , the axial bearing forces P _x1 , P _{x2 of} the two rotor sections cancel 110 . 115 because they are in opposite directions due to the axis of symmetry 120 Bearing fluid flow flowing away on both sides 165 . 166 are directed. As a result, there is no further axial fixation of the rotor 15 in the case 20 necessary.

After flowing through the gap 80 . 105 becomes the bearing fluid flow 165 . 166 again on the input side of the rotor 15 sucked and together with the main fluid flow 160 . 161 condensed again.

Due to the brushless design of the drive unit 35 and the spaced arrangement of the coil ring 130 from the wave 40 can by means of the bearing fluid flow 165 the rotor 15 reliable in the housing 20 stored and at the same time an offset of the axis of rotation 45 of the rotor 15 to a housing axis 195 parallel to the axis of rotation 45 runs, be balanced.

Through the fluid bearing 180 can on other sliding or rolling bearings for storage of the rotor 15 be waived so that the compressor 10 is designed particularly inexpensive. Furthermore, a particularly simple storage, especially in a particularly fast rotating rotor 15 to be provided. Due to the omission of sliding or roller bearings is the compressor 10 overall smaller, so the compressor 10 has a more compact space requirement.

By providing two rotor sections 110 . 115 symmetrical to the axis of symmetry 120 can be completely dispensed with further storage systems. Furthermore, this embodiment has a particularly high flow rate.

4 shows a schematic sectional view through a compressor 200 according to a second embodiment. It is above the axis of rotation 45 the rotor 15 cut and below the axis of rotation 45 shown in plan view. The compressor 200 is essentially identical to the one in 1 shown compressor 10 educated. Deviating from this, the bearing structure 175 additionally herringbone arranged recesses 205 on, the circumferentially evenly spaced on the shroud 75 . 100 are arranged. It should be noted that in 4 the rotor 15 axisymmetric to the symmetry axis 120 is formed, and the recesses 205 also on the right side arranged second rotor section 115 (not shown) are provided. Furthermore, the recesses 205 Of course, be designed as bulges, extending in the direction of the housing part 25 extend radially outward.

The storage structure 175 In the embodiment, it is single row on the shroud 75 . 100 arranged. Of course, it is also conceivable that several rows of the bearing structure 175 in herringbone arranged recesses 205 or bulges circumferentially on the housing part 25 . 30 facing outer peripheral surface of the shroud 75 . 100 are provided. The recesses 205 have a first recess portion 206 and a second recess portion 207 on. The recess sections 206 . 207 include an opening angle α. The opening angle is less than 180 °. The recess sections 206 . 207 are arranged such that the recesses 205 to the direction of rotation of the rotor 15 are open. This allows a particularly high peripheral speed in the bearing fluid flow 165 be induced, so especially in the area of the recesses 205 a particularly stable pressure pad by the bearing fluid flow 165 can be formed, which is the rotor 15 very well stored.

5 shows a sectional view through a compressor 300 according to a third embodiment, wherein the rotor 15 is shown in plan view. The compressor 300 is essentially identical to the ones in the 1 to 4 shown compressors 10 . 200 educated. Deviating from this, the bearing structure 175 bulges 305 on, the spiral circumferentially on the shroud 75 are arranged. The bulges 305 are formed like a shovel. Alternatively, the bulges 305 be connected in the circumferential direction to form a screw. As a result, in a counterclockwise rotation, the bearing fluid flow 165 particularly well in the direction of a radially inwardly disposed on the input side sealing element 310 the bearing structure 170 . 175 be encouraged. The sealing element 310 is formed in the embodiment as a labyrinth seal, whereby a frictional contact between the rotor 15 and the housing 20 can be avoided. This allows a particularly high efficiency of the compressor 300 be ensured. Furthermore, the sealing element 310 the advantage that the bearing fluid flow 165 both from the exit side 55 to the entrance page 50 can be promoted and at the same time by the spiraling design of derecognitions 305 can be accelerated in the circumferential direction. At the same time, the bearing fluid flow accumulates 165 in front of the sealing element 310 on, giving a pressure p _s within the first gap 80 can be kept very high. This allows a stable storage even at low speeds of the rotor 15 be guaranteed.

In the embodiment, the first / second gap 80 . 105 from the exit side 55 to the entrance side 50 formed rejuvenating. Of course, it is also conceivable that the gap 80 . 105 a constant gap width s ₁ , s ₂ across the gap 80 . 105 has away.

It should be noted that the sealing element 310 instead of the input side also at a different position circumferentially on the housing part 25 . 30 or the rotor 15 can be arranged. Of course, it is also conceivable, the sealing element on an in 1 or 2 shown embodiment of the rotor 15 provided. It is also conceivable that the sealing element 310 is waived.

The storage structure 175 is in the 1 to 4 exemplified. Of course, it is also conceivable that differently designed bearing structures are provided, but it is essential that a bearing fluid flow 165 through the storage structure 175 is emphasized, the fluid dynamic bearing between the rotor 15 and the housing 20 provides to sliding or rolling bearings for storage of the rotor 15 to be able to do without.

The drive unit 35 is exemplary in the embodiment. Of course, it is also conceivable that the drive unit 35 is formed differently. The in the 1 to 5 shown drive unit 35 However, has the advantage that by the contactless design of the drive unit 35 between the wave 40 and the coil wreath 130 the wave 40 in the radial direction about the gap width s ₁ , s _{2 is} displaceable, so that depending on the load of the rotor 15 the bearing fluid flow 165 the rotor 15 regardless of the orientation of the compressor 10 . 200 . 300 can store both in the axial and in the radial direction.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited non-patent literature

• EN ISO 25178 [0011]

Claims (10)

Compressor ( 10 ; 200 ; 300 ; 400 ) for a heat pump cycle and / or refrigeration system cycle, comprising a housing ( 20 ) and one about a rotation axis ( 45 ) rotatably mounted rotor ( 15 ), - the housing ( 20 ) at least partially circumferentially of the rotor ( 15 ) is arranged, - wherein the rotor ( 15 ) at least one hub ( 65 . 90 ) and at least one at the hub ( 65 . 90 ) radially outwardly arranged blade ( 70 . 95 ), wherein the blade ( 70 . 95 ) is formed, a main fluid flow ( 160 . 161 ), the rotor ( 15 ) a radially outside of the blade ( 70 . 95 ) arranged shroud ( 75 . 100 ), wherein the shroud ( 75 . 100 ) radially spaced from the housing ( 20 ) is arranged, - wherein radially on the outside of the shroud ( 75 . 100 ) a storage structure ( 170 . 175 ), which is designed to generate a bearing fluid flow ( 165 . 166 ) between the shroud ( 75 . 100 ) and the housing ( 20 ) for forming a fluid dynamic bearing ( 180 ) for the storage of the rotor ( 15 ) in the housing ( 20 ) train. Compressor ( 10 ; 200 ; 300 ; 400 ) according to claim 1, wherein the rotor ( 15 ) an input page ( 50 ) and an output side ( 55 ), wherein the blade ( 70 . 95 ), the main fluid flow ( 160 . 161 ) from the input side ( 50 ) to the output side ( 55 ), the storage structure ( 170 . 175 ), the bearing fluid flow ( 165 . 166 ) from the output side ( 55 ) to the input side ( 50 ) to promote. Compressor ( 10 ; 200 ; 300 ; 400 ) according to claim 2, wherein the input side ( 50 ) radially inside and the output side ( 55 ) radially on the outside of the rotor ( 15 ), wherein the bearing structure ( 170 . 175 ) is at least partially formed spirally. Compressor ( 10 ; 200 ; 300 ; 400 ) according to one of claims 1 to 3, wherein the bearing structure ( 170 . 175 ) a sealing element ( 310 ), wherein the sealing element ( 310 ) between the shroud ( 75 . 100 ) and the housing ( 20 ), wherein the sealing element ( 310 ), the bearing fluid flow ( 165 . 166 ) in the axial direction. Compressor ( 10 ; 200 ; 300 ; 400 ) according to claim 4, wherein the sealing element ( 310 ) is designed as a labyrinth seal. Compressor ( 10 ; 200 ; 300 ; 400 ) according to one of claims 1 to 5, wherein the bearing structure ( 170 . 175 ) is formed herringbone-like, and / or wherein the bearing structure ( 170 . 175 ) has a surface roughness in the range of 1 Rz to 60 Rz. Compressor ( 10 ; 200 ; 300 ; 400 ) according to one of claims 1 to 6, wherein the bearing structure ( 170 . 175 ) at least one recess ( 205 ) and / or a bulge ( 305 ) which is oblique or transverse to the circumferential direction of the hub ( 65 . 90 ) is arranged. Compressor ( 10 ; 200 ; 300 ; 400 ) according to one of claims 1 to 7, wherein the rotor ( 15 ) another hub ( 90 ), wherein at the further hub ( 90 ) at least one radially outer side arranged further blade ( 95 ), the further blade ( 95 ) is formed, another main fluid flow ( 161 ), whereby the further hub ( 90 ) with the hub ( 65 ) over a wave ( 40 ), wherein the rotor ( 15 ) a radially outside of the further blade ( 95 ) arranged further shroud ( 100 ), wherein the further shroud ( 100 ) radially spaced from the housing ( 20 ) is arranged, - wherein the housing ( 20 ) the further shroud ( 100 ) at least partially surrounds the circumference, - wherein radially on the outside of the other shroud ( 75 . 100 ) another storage structure ( 175 ) is provided, which is formed, another Lagerfluidstrom ( 166 ) between the other shroud ( 75 . 100 ) and the housing ( 20 ). Compressor ( 10 ; 200 ; 300 ; 400 ) according to claim 8, wherein the further bearing structure ( 175 ) and the storage structure ( 170 ) axisymmetric to one between the two hubs ( 65 . 90 ) arranged symmetry axis ( 120 ) are formed. Compressor ( 10 ; 200 ; 300 ; 400 ) according to claim 8 or 9, wherein on the shaft ( 40 ) between the two hubs ( 65 . 90 ) at least one magnet ( 125 ), wherein the magnet ( 125 ) torque-locking with the shaft ( 40 ), wherein radially outwardly of the shaft ( 40 ) at least one coil ring ( 130 ) is provided for providing an alternating magnetic field, wherein the alternating magnetic field is formed, in operative connection with the magnet ( 125 ) to a rotational movement of the rotor ( 15 ).

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