DE102005052623B4 - compressor - Google Patents

Abstract

This invention relates to a compressor (1) with a housing (3, 19, 96, 97; 103; 203) which has a housing axis (4) and a housing inner wall (3; 203; 303). The compressor further comprises a Mambran (7; 207), a roller holder (5, 95; 105; 208; 308, 319, 381, 382, 383, 384, 385, 386), which is mounted so that it is around the housing axis (4) is rotatable and has a roller (61, 71, 81; 271, 272, 273, 274, 275, 276; 371, 372, 373, 374, 375, 376) with a roller axis (62, 72, 82), which is pressed by the roller holder against the membrane, the roller axis not coinciding with the housing axis (4), the roller pressing the membrane (7; 207) against the inner wall of the housing. The membrane is attached to a first number of webs (16, 26, 36, 46, 56; 216, 226, 236, 246, 256, 266) in a fluid-tight manner on the housing inner wall (3; 203; 303), the webs in a Plane perpendicular to the housing axis lie on a circle and form an equilateral polygon.

Description

The This invention relates to the technical field of compressors, in particular diaphragm pumps, peristaltic pumps and peristaltic pumps.

A generic compressor is from the FR 1.330.187 A , especially 3 and the corresponding part of the description.

Among other things, rotary vane pumps are known. By way of example in this context is the US 4,514,153 A cited. This rotary vane pump has a total of three chambers. In each chamber, three staggered by 120 ° with respect to a rotational axis arranged slide are provided. The first two chambers have a common inlet and outlet, wherein the slides of the first chamber are arranged offset by 60 ° with respect to the axis of rotation relative to the slides of the second chamber. An eccentrically arranged with respect to the axis of rotation of the slide rotor rotates in operation with the sliders and forms the inner boundary of a pumping chamber. The outer boundary of the pumping chamber is formed by the pump housing. The rotor has a slot-shaped opening with a guide channel for each slide. Each slider is sealed by two sealing strips opposite the rotor. Since the rotor and the slide have different axes of rotation, depending on the angle, a slider projects out of the rotor to different extents. The inner wall of the pump housing is rotationally symmetrical with the exception of the areas of the inlet and outlet formed to the axis of rotation of the slide, so that the slide is largely sealed with the inner wall of the pump housing.

The US 4,551,073 A describes several embodiments of pumps for liquid and gaseous fluids, in particular blood. In one embodiment, the interior of a pump housing is designed in the form of a 2-lobed trochoid. The rotary piston is 3-lobed. Within the rotary piston, a motor is housed. The housing of the motor is rotatably mounted relative to the rotary piston. The rotation of the motor shaft is transmitted via a two-stage planetary gear to the motor housing, wherein the axes of the planet gears are mounted in the rotary piston. The output takes place via a gearwheel attached to the motor housing, which engages in an inner ring gear attached to the rotary piston.

In the US 4,551,073 A another embodiment described in which the pump housing is 1-lobed and the piston has 2 edges. The latter embodiment is also in the US 4,594,060 A described.

The DE 29 09 228 A1 describes a working machine for compressing and conveying fluids of all kinds. The described embodiments comprise a housing in which there is a piston, which is formed as an elastically deformable ring. Between the piston and the housing arise suction chambers and pressure chambers, which are separated by separating elements such as swing vanes or separating slide. The piston is deformed, for example, by 3 rollers located in the piston and pressed against the inside wall of the housing at three points. These rollers lie against a freely rotatably mounted support member, which is designed as a thin-walled tube. In addition, three support rollers are provided between the rollers, which prevent an inadmissible deflection of the piston. These support rollers are only touched under load.

A similar embodiment is in CH 25 072 A described. In this heat engine, a belt is pressed by three rollers from the inside against a ring. The band is connected in two places with the ring by a respective clamping piece.

The CH 327 446 A describes a compressed air motor. In a housing, a hollow cylinder is rotatably mounted, which carries in its central longitudinal bore a rotatable control member. On the hollow cylinder is a jacket made of flexible plastic, which is divided by längsachsparallel directed ribs in three equal sections. The individual, each lying between two ribs cells are associated with inflow and outflow channels, which cooperate with control breakthroughs of the control member. In the housing, supporting surfaces forming rollers are easily rotatably mounted on opposite sides of the hollow cylinder. In addition, the housing includes the support rollers associated pairs of rollers, each leading an endless belt.

The GB 179,324 A describes gas and air compressors or blowers. In a cylindrical housing, a belt is pressed by two rollers against the inner wall of the housing. The belt forms a loop and is connected at one point to the inner wall of the housing. An outlet is provided with a check valve.

The FR 1.330.187 A describes a pump in which an elastic band is pressed by four rollers of them against a cylindrical wall. Rods attach the elastic band to the wall in three places.

In the prior art, a variety of forms of planetary gears are also known. The Harmonic Drive micro-AC servo drive with hollow shaft is (or was) considered to be the smallest positioning drive in the world with a length of 6 mm and a diameter of approx. 2 mm. For reduction, here is a planetary gear be used.

The OECHSLER AG offers a reduction gear under the brand WAVE DRIVE at. In a deformable ram is mounted with the drive shaft firmly connected, elliptical drive core. Due to the rotational movement of the ellipse, an elastic toothed ring is produced via the ram wheel continuously deformed and engages in a housing-fixed internal toothing. Between External and internal toothing exists a tooth number difference, which causes a slow relative movement.

In geometry there are round and elliptical cylinders. Its lateral surface is defined by the following equation: (Ax) 2 + (by) 2 = d> 0 (1)

It is a round cylinder if a = b, otherwise it is an elliptical cylinder.

It It is an object of the invention to provide a novel rotary piston compressor to avoid slippage between the rollers and the diaphragm.

These Task is solved by the teaching of claim 1.

preferred embodiments The invention are the subject of the dependent claims.

Of the Use of a plurality of separate chambers allows in advantageously a uniform promotion a fluid. It can the chambers are formed between a membrane and a housing inner wall. The membrane is in this case with the housing inner wall at an upper and lower inner edge and connected to webs fluid-tight.

Especially if a roll, the membrane is largely close to the housing inner wall expresses are only at the outlets the chambers need valves. This advantageously reduces the number of parts.

Especially Easy to make are round inner walls and round, cylindrical rollers.

If the number of chambers equal to two times the number of roles minus one is, each chamber is in a different pumping phase, so that the promotion the fluid is optimally uniform.

to Absorption of radial forces can be installed advantageously a round cylinder, its axis with the housing axis coincides and on which roll the round rolls.

Around at given housing dimensions to a larger chamber volume to come, can Rolls are used, which take the form of an elliptical cylinder to have. The housing inner wall then has corresponding bulges between the webs, so that the rollers can roll on a round sun gear or when turning around its own roller axis, the membrane straight to the with bulges provided housing inner wall to press.

in the Below is a preferred embodiment of the invention below With reference to the accompanying drawings explained in more detail. Showing:

1 a section through a first embodiment of a rolling piston diaphragm pump according to the invention perpendicular to the housing axis;

2 a section through the first embodiment of the rolling piston diaphragm pump according to the invention along the housing axis;

3 a section through a second embodiment of the invention Rollkolbenmembranpumpe perpendicular to the housing axis;

4 a section through a third embodiment of the rolling piston diaphragm pump according to the invention perpendicular to the housing axis;

5 a section through a fourth embodiment of the invention Rollkolbenmembranpumpe perpendicular to the housing axis;

in the The following will denote the same parts by the same reference numerals, and the like Parts by similar Reference numeral. The terms pump and compressor are used used synonymously.

1 shows a first embodiment of a rolling piston diaphragm pump 1 in a section perpendicular to a housing axis 4 along the line II-II in 2 , 2 shows a section through the rolling piston diaphragm pump 1 along the line II in 1 , The rolling piston diaphragm pump 1 includes a pump housing 2 with a round, cylindrical inner wall 3 , an elastic membrane 7 , three rolling-piston 61 . 71 . 81 and a lower and an upper disc 5 respectively. 95 ,

The axes 62 . 72 . 82 the rolling piston are in each case an upper roller bearing z. B. 73 and a lower roller bearing z. B. 74 for example, rotatably mounted in a ball bearing. The distance between the rolling piston axles 62 . 72 . 82 from the inner wall 3 is a little smaller than the radius of a rolling piston plus the membrane thickness, so that the membrane there fluid-tight with the inner wall 3 completes where a rolling piston the membrane 7 against the inner wall 3 suppressed.

The inner wall 3 has a total of five keyhole-shaped recesses 18 . 28 . 38 . 48 . 58 in each of which one of a total of five bars 16 . 26 . 36 . 46 . 56 is attached. Without deformation by the rolling piston, the membrane would 7 halfway up the inner wall 3 form an equilateral pentagon. The inner wall 3 has an upper and a lower edge, both of which are circular. As in 2 is shown, the membrane is pulled on the upper and lower edge and is there with the inner wall 3 connected. This results in a total of five chambers 11 . 21 . 31 . 41 and 51 ,

Each of the chambers 11 . 21 . 31 . 41 and 51 has an inlet 12 . 22 . 32 . 42 respectively. 52 and an outlet 13 . 23 . 33 . 43 respectively. 53 on. Currently it is planned to switch the individual chambers in parallel. The number of chambers and the number of rolling piston is chosen to be strange, so that each chamber is in a different pumping phase. These measures contribute to the most uniform possible fluid flow.

In a parallel connection of the chambers, it is only at the outlets 13 . 23 . 33 . 43 and 53 required to install valves. In 1 is merely an example of the exhaust valve 14 at the outlet 13 the chamber 11 shown. The outlet valve 14 includes a ball 15 and a spring that presses the ball against a valve seat. Exemplary is at the inlet 12 the chamber 11 an inlet valve 17 with a hinged or deformable membrane that can also be used on the outlets.

As in 1 by way of example at inlet 12 and outlet 13 shown, the inner wall can 3 of the pump housing 2 be chamfered at the inlets and outlets and / or in a groove parallel to the adjacent lands 16 or 26 into the inlets and / or outlets to reduce the flow resistance at the inlets and outlets.

Considering the dimensions of the rolling piston, the following choice seems advantageous: K = 2R - 1 (2)

K is the number of chambers and R denotes the number of rolling piston. Taking into account the extensibility limits of the membrane 7 and geometry, a scroll piston diaphragm pump with only two rotary pistons and three chambers appears to be difficult to implement and has an unacceptably high pulsation of fluid flow for some applications. On the other hand, the larger the number of chambers is chosen, the smaller the chamber volume. The ratio between chamber volume and dead volume at the end of a compression process gives the maximum ratio of pressure at the outlet to pressure at the inlet. The larger the number of chambers is chosen, the lower the achievable pressure with otherwise the same parameters. In addition, the total volume of the chambers decreases with increasing number of chambers with otherwise identical parameters. Therefore, the funded total flow decreases with increasing number of chambers. Therefore, scroll piston diaphragm pumps with three rotary pistons and five chambers as in 1 presented or with four rolling piston and seven chambers to represent a good compromise between the different requirements.

With one revolution of the discs 5 and 95 15 times the chamber volume is promoted. In one embodiment, with seven chambers and four rolling pistons, one turn of the discs 5 and 95 even 28 times that - then smaller - chamber volume promoted.

2 shows a section through the first embodiment of the rolling piston diaphragm pump 1 along the line II in 1 , The rolling piston 72 is shown cut. He is in an upper roller bearing 73 in the upper disc 95 and in a lower roller bearing 74 in the lower disc 5 rotatably mounted for example in ball bearings. The rolling pistons are driven over the two discs 5 and 95 , which in turn firmly on an axis 91 are mounted. In 2 are the lower disc 5 and the axis 91 made in one piece. The axis 91 is mounted in the housing by ball bearings.

The housing consists of a housing foot 96 , a pump housing 2 a sprocket 19 with internal teeth, and a housing cover 97 , Also, the rolling piston are with sprockets 65 . 75 provided in the sprocket 19 intervention. This ensures that the relative angular velocity with respect to the housing axis 4 between pump housing 2 and the area of the rolling piston, the inner wall of the pump housing 2 is closest, approximately 0.

The control of the rotational speed of the rolling piston on the sprockets ensures that the diaphragm 7 only by the position of the rolling piston is stretched and not even by the force required to turn a rolling piston. The latter force is mainly generated by the fact that the rolling piston 61 . 71 . 81 the membrane 7 largely close to the inner wall of the pump housing 2 have to press while keeping the diaphragm 7 in radial Direction something is squeezed. According to current knowledge, this flexing work is best achieved by an additional torque transmission through the sprockets 19 . 65 and 75 controlled.

If the friction between the membrane 7 and the rolling piston 61 . 71 . 81 sufficient, the sprockets 19 . 65 and 75 omitted. However, as things currently stand, it seems difficult to have a material for the membrane 7 to find, on the one hand sufficiently elastic for the deformations during the pumping operation and on the other hand sufficiently rigid to drive the rolling piston. To the friction between the membrane 7 and the rolling piston 61 . 71 . 81 can increase the membrane 7 and the rolling piston 61 . 71 . 81 be provided with interlocking teeth. In particular, a round toothing, as used in Power Grip HTD timing belt into consideration.

3 shows a section through a second embodiment of a rolling piston diaphragm pump according to the invention 101 , The second embodiment differs from the first in that the lower disc 5 and the top disc 95 through a lower guide ring 105 or an upper guide ring (not shown) to be replaced. Besides, the axis forms 91 in the area between the upper and lower edge of the pump housing 2 a solar cylinder 108 , With sufficient friction between the solar cylinder 108 and the rolling piston 61 . 71 . 81 can the solar cylinder 108 as a drive for the rolling piston 61 . 71 . 81 be used. If the sun cylinder 108 and the rolling piston 61 . 71 . 81 made of metal, the friction should hardly be large enough. That is why in the plane of the sprocket 19 a sun gear 109 used that firmly with the axle 91 is connected and in the sprockets 65 and 75 intervenes.

The purpose of the solar cylinder 108 In this embodiment, it is mainly to absorb the radial forces coming from the inner wall 3 of the pump housing 2 over the pinched and stretched membrane 7 on the rolling piston 61 . 71 . 81 be transmitted. This relieves the roller piston bearings in the guide rings. This relief can also be found in the 1 and 2 illustrated embodiments can be realized by a hollow cylinder on which the rolling piston supported and in the hole, the axis 91 can turn.

Whether one chooses the first or second embodiment, depends on the adaptation between the engine and the rolling piston diaphragm pump in terms of speed and torque. The speed ratio between the first and second embodiments results from the quotient of the radius of the sun gear 108 divided by the distance between the rolling piston axes 62 . 72 . 82 from the housing axis 4 , It is assumed that the effective radii of the teeth of the sun gear 109 , the sprockets 75 and 65 and the sprocket 19 lead to no other result. Otherwise, the pump jams. The torque ratio is just the reciprocal of the speed ratio.

From these considerations it follows that you can fine tune the engine and pump in the first embodiment by the distance of the rolling piston axes 62 . 72 . 82 from the housing axis 4 at given radius of the inner wall 3 can make. In the second embodiment, this fine tuning can be achieved by the radius of the sun cylinder 108 at a given radius of the inner wall 3 respectively. In both cases, this results in additional consideration of the ceiling of the membrane 7 the radius of the rolling piston 61 . 71 . 81 ,

At all in connection with the 1 to 3 described embodiments, the center of gravity of the rolling piston rests. An imbalance arises only through the deformation of the light membrane and movements in the valves. The described scroll piston diaphragm pumps therefore have a very smooth running.

4 shows a third embodiment of a rolling piston diaphragm pump 201 , The difference to the two previous embodiments is mainly that the inner wall 203 of the pump housing 2 does not have a circular cross-section and the rolling pistons are elliptical cylinders. The inner wall 203 of the pump housing 2 points between the bars 216 . 226 . 236 . 246 . 256 . 266 Bulges on the volume of the chambers 211 . 221 . 231 . 241 . 251 . 261 enlarge. The rolling piston 271 . 272 . 273 . 274 . 275 . 276 roll on the sun wheel 208 from. The exact shape of the inner wall 203 results as Abrollform the rolling piston on the sun gear, taking into account the thickness of the membrane 207 , Also the inlets 212 . 222 . 232 . 242 . 252 . 262 and the outlets 213 . 223 . 233 . 243 . 253 . 263 are shown schematically.

At the in 4 illustrated embodiment are each two opposite chambers, so the first chamber 211 and the fourth chamber 241 , the second chamber 221 and the fifth chamber 251 as well as the third chamber 231 and the sixth chamber 261 in the same pumping phase. This ensures that the system's center of gravity rests and the scroll piston diaphragm pump 201 generates low vibrations during operation. In another embodiment, the pumping phases between the individual chambers may be offset by 60 ° to produce a more uniform fluid flow.

The rolling piston 271 . 272 . 273 . 274 . 275 . 276 be from the sun gear 208 driven. To properly unwind the rolling piston between the sun gear 208 , the inner wall 203 as well as the membrane 207 can ensure the sun gear 208 , the rolling piston 271 . 272 . 273 . 274 . 275 . 276 as well as the membrane 207 with a toothing, in particular a round toothing, as used in Power Grip HTD timing belt are provided. In another embodiment, the gears may be similar as in FIG 2 be arranged in a different plane than the membrane plane. In this plane can be a similar area as the inner wall 203 with an internal toothing similar to the sprocket 19 be provided. The sun wheel 208 as well as the rolling piston 271 . 272 . 273 . 274 . 275 . 276 have external teeth in this plane, which engage with each other. Finally, gears can be completely absent if the friction between the rolling piston 271 . 272 . 273 . 274 . 275 . 276 and the membrane 207 as well as the sun wheel 208 and the rolling piston 271 . 272 . 273 . 274 . 275 . 276 is large enough and the membrane is thick enough to compensate for phase errors. Thus, phase errors do not accumulate over several revolutions, which would lead to jamming of the pump.

5 shows a fourth embodiment of a rolling piston diaphragm pump, the second embodiment in 3 and the third embodiment in FIG 4 combined. Similar to the second embodiment, the rolling piston axes 391 . 392 . 393 . 394 . 395 . 396 the rolling piston 371 . 372 . 373 . 374 . 375 . 376 rotatably mounted in two guide rings, not shown. The rolling piston 371 . 372 . 373 . 374 . 375 . 376 put themselves in the area of the membrane 207 elliptical cylinders. Since the rolling piston 371 . 372 . 373 . 374 . 375 . 376 are stored on their axes and do not roll on a sun gear, is at the same ratio of the short and long radius of the elliptical cylinder and otherwise the same parameters, the volume of the chambers 211 . 221 . 231 . 241 . 251 . 261 smaller than the second embodiment in FIG 3 , The sprocket 319 is stationary and can be like the sprocket 19 Be part of the housing. The rolling pistons are from the sun gear 308 over the planet wheels 381 . 382 . 383 . 384 . 385 . 386 driven. The rolling pistons slide over the membrane 207 and push the fluid in front of you. This movement plus the thickness of the membrane 207 define the exact shape of the inner wall 303 ,

Because the rolling piston 371 . 372 . 373 . 374 . 375 . 376 in their axes 391 . 392 . 393 . 394 . 395 . 396 are stored, resting neglecting the movements of the membrane 207 the system focus. Therefore, in this embodiment, it is advantageous to select the phase offset between two chambers equal to 60 ° in order to achieve the most uniform possible fluid flow.

Also the inlets 212 . 222 . 232 . 242 . 252 . 262 and the outlets 213 . 223 . 233 . 243 . 253 . 263 are in 5 schematically drawn.

At all in connection with the 1 to 5 described embodiments, the chambers can also be connected in series. This increases the total pressure achieved and the waviness of the fluid flow. When connected in series, the pumping process in all chambers should be in phase. Therefore, in a series connection of the chambers, the number of rolling piston is equal to the number of chambers selected. Since the inlet of a subsequent chamber is connected via a valve to the outlet of the preceding chamber, the number of valves is equal to the number of chambers. As a rule, no valve is needed at the inlet of the first chamber.

If the inlets and outlets close to the bars, no valves are required there a rolling piston first the outlet of a previous chamber and shortly thereafter the inlet the subsequent chamber largely tightly closes.

The Membrane should be self-contained Reset. This can be done with the help of a suitable fabric or a leaf spring happen. The leaf springs can either be housed in the individual chambers or in the Membrane to be integrated.

The For example, membrane may be made of butadiene rubber, chloroprene rubber, Silicone rubber or polyurethane rubber are produced.

at all described embodiments can ever according to requirements, in particular to the noise level, straight-, oblique-, arrow- and double helical gears are used unless otherwise stated. It will an involute toothing opposite a Zykloidenverzahnung due to the simpler manufacturing and the greater insensitivity across from Axial distance errors preferred. For a low noise level To achieve that, should be gears made of metal with gears be combined from plastic.

Targeted Performance data of the compressors described in this application are a volume flow of 40 l / min, a pressure of (1.25 ± 0.25) cash on promotion of air, a noise level of 30 dBA, a life of 10,000 h, a length less than 0.1 m, a width less than 0.12 m and a height less than 0.12 m.

The invention has been explained in detail above with reference to preferred embodiments. For However, one skilled in the art will appreciate 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.

1

Rotary piston diaphragm pump

2

pump housing

3

cylindrical inner wall

4

housing axis

5

(lower) disc

7

membrane

11

first chamber

21

second chamber

31

third chamber

41

fourth chamber

51

fifth chamber

12 22, 32, 42, 52

inlet

13 23, 33, 43, 53

outlet

14

outlet valve

15

Bullet

16 26, 36, 46, 56

web

17

intake valve

18 28, 38, 48, 58

recess

19

sprocket

61

first rolling piston

71

second rolling piston

81

third rolling piston

62 72, 82

 Roll piston axes

73

upper Roll piston bearing

74

lower Roll piston bearing

65, 75

sprocket

91

axis

92

upper Achslager

93

lower Achslager

95

(upper) disc

96

Case foot

97

housing cover

105

guide ring

108

solar cylinder

109

sun gear

201

Rotary piston diaphragm pump

202

pump housing

203

inner wall

207

membrane

208

sun

211

first chamber

221

second chamber

231

third chamber

241

fourth chamber

251

fifth chamber

261

sixth chamber

212 222, 232, 242, 252, 262

inlet

213 223, 233, 243, 253, 263

outlet

216 226, 236, 246, 256, 266

web

271, 272, 273, 274, 275, 276

 chamber

301

Rotary piston diaphragm pump

302

pump housing

303

inner wall

319

sprocket

308

sun

371, 372, 373, 374, 375, 376

rolling piston

381, 382, 383, 384, 385, 386

planet

391, 392, 393, 394, 395, 396

Roll the piston axis

Claims (11)

Compressor ( 1 ) with: a housing ( 3 . 19 . 96 . 97 ; 103 ; 203 ) with a housing axis ( 4 ) and a housing inner wall ( 3 ; 203 ; 303 ); a membrane ( 7 ; 207 ), which by means of webs ( 16 . 26 . 36 . 46 . 56 ; 216 . 226 . 236 . 246 . 256 . 266 ) fluid-tight to the housing inner wall ( 3 ; 203 ; 303 ), wherein the webs lie in a plane perpendicular to the housing axis on a circle and form an equilateral polygon; a roll holder ( 5 . 95 ; 105 ; 208 ; 308 . 319 . 381 . 382 . 383 . 384 ; 385 . 386 ), which is mounted so that it around the housing axis ( 4 ) is rotatable; and at least one role ( 61 . 71 . 81 ; 271 . 272 . 273 . 274 . 275 . 276 ; 371 . 372 . 373 . 374 . 375 . 376 ) with a roller axle ( 62 . 72 . 82 ) from the roll holder ( 5 . 95 ; 105 ; 208 ; 308 . 319 ; 381 . 382 . 383 . 384 . 385 . 386 ) against the membrane ( 7 ; 207 ), the roller axis ( 62 . 72 . 82 ) not with the housing axis ( 4 ), where the roll is the membrane ( 7 ; 207 ) presses against the housing inner wall; characterized in that the roller is a sprocket ( 65 . 75 ) and the housing ( 3 . 19 . 96 . 97 ) a sprocket ( 19 ) having internal teeth, wherein the sprocket ( 65 . 75 ) of the roller in the sprocket ( 19 . 319 ) of the housing ( 3 . 19 . 96 . 97 ) engages, wherein the circumference of the sprocket ( 19 ) of the housing ( 3 . 19 . 96 . 97 ) approximately equal to the circumference of the housing inner wall ( 3 ; 203 ). Compressor according to claim 1, characterized in that the housing inner wall ( 3 ; 203 ; 303 ) has an upper and a lower edge, wherein the membrane ( 7 ; 207 ) is fluid-tightly connected to the upper and lower edges, wherein the upper and lower edge through the webs ( 16 . 26 . 36 . 46 . 56 ; 216 . 226 . 236 . 246 . 256 . 266 ) is connected so that between the membrane ( 7 ; 207 ) and the hous his wall ( 3 ; 203 ; 303 ) separate chambers ( 11 . 21 . 31 . 41 . 51 ; 211 . 221 . 231 . 241 . 251 . 261 ) are located. Compressor according to claim 2, characterized in that each chamber has an inlet ( 12 . 22 . 32 . 42 . 52 ; 212 . 222 . 232 . 242 . 252 . 262 ) and an outlet ( 13 . 23 . 33 . 43 . 53 ; 213 . 223 . 233 . 243 . 253 . 263 ), wherein. each outlet a valve ( 14 . 15 ) which allows fluid to flow out of the chamber only. Compressor according to claim 2 or 3, characterized in that a) the housing inner wall ( 3 ) is cylindrical between the upper and lower edges; and b) the roles ( 61 . 71 . 81 ) between the upper and lower edge have the shape of a cylinder with a circular cross section with a cylinder axis and in the roll holder ( 5 . 95 ; 105 ) are rotatably mounted about the cylinder axis. Compressor according to one of claims 2 to 4, characterized in that the number of chambers ( 11 . 21 . 31 . 41 . 51 ) twice the number of rolls ( 61 . 71 . 81 ) minus one. Compressor according to one of the preceding claims, characterized in that a drive axle ( 91 ) rotatably with the roll holder ( 5 . 95 ; 105 ) connected is. Compressor according to one of claims 1 to 5, characterized in that a drive axle ( 91 ) a sprocket ( 109 ), in the sprockets ( 65 . 75 ) engage rollers, wherein the sprocket of the drive axle ( 91 ) a sun gear and the sprockets ( 65 . 75 ) of the rollers represent planet wheels. A compressor according to claim 7, wherein between the upper and lower edges of a central support cylinder ( 108 ) on which the rollers ( 61 . 71 . 81 ) can roll during operation, wherein the axis of the support cylinder ( 108 ) coincides with the housing axis, so that the support cylinder ( 108 ) a sun gear and the rollers ( 61 . 71 . 81 ) Represent planet gears. Compressor according to one of claims 2 or 3, characterized in that the rollers ( 271 . 272 . 273 . 274 . 275 . 276 ; 371 . 372 . 373 . 374 . 375 . 376 ) between the upper and lower edge have the shape of a cylinder with elliptical cross-section. Compressor according to claim 9, characterized in that the rollers ( 271 . 272 . 273 . 274 . 275 . 276 ) from the membrane ( 7 ) against a sun wheel ( 208 ), whereby the housing inner wall ( 203 ) between the bridges ( 216 . 226 . 236 . 246 . 256 . 266 ) Bulges outwards, which are dimensioned so that the rollers when rolling between membrane ( 7 ) and sun gear ( 208 ) upon rotation of the sun gear ( 208 ) press the membrane straight against the housing wall. Compressor according to claim 9, characterized in that the sprockets ( 381 . 382 . 383 . 384 . 385 . 386 ) of the roles ( 371 . 372 . 373 . 374 . 375 . 376 ) outside in the internal toothing of the sprocket ( 319 ) of the housing ( 3 . 19 . 96 . 97 ) and inside the toothing of a sun gear ( 308 ), wherein the housing inner wall ( 303 ) between the bridges ( 216 . 226 . 236 . 246 . 256 . 266 ) Bulges outwards, which are dimensioned so that the rollers when rolling between the sprocket ( 319 ) of the housing ( 3 . 19 . 96 . 97 ) and sun gear ( 308 ) upon rotation of the sun gear ( 308 ) press the membrane straight against the housing wall.