COMPRESSOR, AND VEHICLE COMPRESSED AIR SYSTEM WITH A COMPRESSOR OF THIS TYPE

Abstract

A compressor for providing compressed air for a vehicle compressed air system has an inlet chamber formed by an inlet chamber wall and provided with an inlet opening for taken-in air, and an outlet chamber defined by an outlet chamber wall and provided with an outlet opening for air compressed by the compressor. Furthermore, the compressor has a heat flow reduction device which is designed to reduce at least one of a heat flow from a component, connected to the inlet chamber wall, of the compressor to the taken-in air in the inlet chamber and a heat flow from the compressed air in the outlet chamber to a component, connected to the outlet chamber wall, of the compressor.

Description

FIELD

Disclosed embodiments relate to a compressor and a vehicle compressed air system with a compressor of this type, in particular for rail vehicles.

BACKGROUND

Effective compression in modern compressors presupposes a high mass flow. To this end, it is required for heating of a medium to be compressed to be kept as low as possible before and during the compression. For this purpose, it is known in the prior art for a water cooling system to be used which, in addition to component cooling, also designs the process of compression more efficient in this regard.

In modern rail vehicles, however, an air-cooled compressor is the rule, since a water cooling system requires additional outlay for additionally used components and in the case of the installation into the rail vehicles.

SUMMARY

Therefore, disclosed embodiments provide an inexpensive compressor for a vehicle compressed air system, which compressor makes an efficient compression process possible.

BRIEF DESCRIPTION OF THE FIGURES

In the following text, disclosed embodiments are explained on the basis of exemplary embodiments with reference to the drawings, in which, in particular:

FIG. 1 diagrammatically shows a vehicle compressed air system with a compressor in a sectional illustration with a connector portion and a part of a compression space housing and heat flows which occur in the compressor,

FIG. 2 shows a first embodiment of a compressor,

FIG. 3 shows one variant of the first embodiment (shown in FIG. 2) of the compressor,

FIG. 4 shows a second embodiment of the compressor,

FIG. 5 shows a third embodiment of the compressor,

FIG. 6 shows a fourth embodiment of the compressor,

FIG. 7 shows a fifth embodiment of the compressor,

FIG. 8 shows a sixth embodiment of the compressor, and

FIG. 9 shows a seventh embodiment of the compressor.

DETAILED DESCRIPTION

In accordance with at least one disclosed embodiment, a compressor for providing compressed air for a vehicle compressed air system has an inlet chamber which is formed by an inlet chamber wall and is provided with an inlet opening for sucked-in air, and an outlet chamber which is formed by an outlet chamber wall and is provided with an outlet opening for air compressed by the compressor. The compressor has, furthermore, a heat flow reduction device which is configured to reduce a heat flow from a component of the compressor which is connected to the inlet chamber wall to the sucked-in air in the inlet chamber, and/or a heat flow from the compressed air in the outlet chamber to a component of the compressor which is connected to the outlet chamber wall.

The heat flow reduction device which reduces the heat flow from a component which is connected to the inlet chamber to the sucked-in air in the inlet chamber can prevent the air in the inlet chamber from being heated excessively. If, furthermore, in addition or as an alternative, a heat flow reduction device is provided which reduces the heat flow from the compressed air in the outlet chamber to a component which is connected to the outlet chamber wall, the effect of the prevention of the excessive heating can be achieved in an alternative manner or to a greater extent.

In one advantageous refinement of the compressor, the heat flow reduction device has at least parts of the inlet chamber wall and the outlet chamber wall which are configured such that a first air gap is configured between two opposite surfaces of the outlet chamber wall and the inlet chamber wall.

For the case where the inlet chamber and the outlet chamber are provided in a common housing, such as for instance a cylinder head with a common inlet chamber wall and outlet chamber wall which is then one and the same wall, this arrangement can greatly reduce the great heat flow from the outlet chamber to the inlet chamber.

In the case of one advantageous refinement of the compressor, the inlet chamber wall and the outlet chamber wall are configured as separate components.

The separation of the inlet chamber and the outlet chamber ensures a reduction in the heat flow, and the respective components can be of optimum design, since their shapes can be adapted individually to a suitable shape of the inlet and outlet chamber.

In accordance with another advantageous refinement of the compressor, the inlet chamber wall and the outlet chamber wall are formed integrally, and the first air gap is configured in such a way that the inlet chamber wall and the outlet chamber wall are spaced apart from one another at least partially.

This refinement makes a reduction of components and simplified assembly possible.

In a further advantageous refinement, the compressor has a connector portion which has the inlet chamber and the outlet chamber, a compression space housing which is configured such that the sucked-in air is compressed therein, and has a valve plate between the connector portion and the compression space housing, with the result that the valve plate forms a portion of the inlet chamber wall and the outlet chamber wall, the heat flow reduction device having a first thermal insulation material at least between one of the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side.

If the first thermal insulation material is provided between the inlet chamber wall and the valve plate, the heat flow from the valve plate to the inlet chamber wall is reduced, with the result that heating of the inlet chamber wall is reduced and the heat flow to the gas to be sucked in is also reduced. In the case of a provision of the thermal insulation material between the outlet chamber wall and the valve plate, the heat flow to the valve plate is reduced in addition or as an alternative.

In the case of a further advantageous refinement of the compressor, the first thermal insulation material is provided between both the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side.

As a result of this measure, both the heat flow from the outlet chamber wall to the valve plate and the heat flow from the valve plate to the inlet chamber wall are reduced.

In accordance with a further advantageous refinement, the compressor has a connector portion which has the inlet chamber and the outlet chamber, a compression space housing which is configured such that the sucked-in air is compressed therein, and a valve plate between the connector portion and the compression space housing, with the result that a first contact surface is formed between the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side. The heat flow reduction device has a first cutout in at least one of the inlet chamber wall, the outlet chamber wall and the valve plate next to the first contact surface, such that the first cutout is configured to form a second air gap next to the first contact surface.

As a result of the provision of the second air gap, the first contact surface between the inlet chamber wall or the outlet chamber wall on one side and the valve plate on the other side is reduced, with the result that the heat flow from the valve plate to the inlet chamber wall or from the outlet chamber wall to the valve plate is also reduced, in order to reduce a transfer of heat from the air in the outlet chamber to the air in the inlet chamber.

In a further advantageous refinement, the compressor has a compression space housing which is configured such that the sucked-in air is compressed therein, and the heat flow reduction device has a second thermal insulation material between at least one of the inlet chamber wall and the outlet chamber wall on one side and the compression space housing on the other side.

In this refinement, firstly a heat flow from the outlet chamber via the compression space housing to the inlet chamber is reduced. Moreover, a heat flow via the compression space housing to individual components of the compressor such as, for instance, a piston ring, a piston coating or a bearing is reduced, with the result that their thermal loading is reduced and a separate cooling system can be dispensed with.

In accordance with a further advantageous embodiment, the compressor has a compression space housing which is configured such that the sucked-in air is compressed therein, a second contact surface being formed between the compression space housing on one side and the inlet chamber wall and the outlet chamber wall on the other side, and the heat flow reduction device having, in at least one of the inlet chamber wall, the outlet chamber wall and the compression space housing, next to the second contact surface, a second cutout which is configured such that a third air gap is formed next to the second contact surface.

As a result of the third air gap, the contact surface between at least one of the inlet chamber wall and the outlet chamber wall and the compression space housing is reduced, with the result that the heat flow from the outlet chamber wall to the compression space housing and from the compression space housing to the inlet chamber wall is also reduced. Moreover, a heat flow via the compression space housing to individual components of the compressor such as, for instance, a piston ring, a piston coating or a bearing is reduced, with the result that their thermal loading is reduced and a separate cooling system can be dispensed with.

In a further advantageous refinement, the compressor has a connector portion which has the inlet chamber and the outlet chamber, a compression space housing which is configured such that the sucked-in air is compressed therein, and a valve plate between the connector portion and the compression space housing, and, as the heat flow reduction device, the valve plate contains a region which projects from the connector portion and the compression space housing.

By way of a valve plate which is designed in this way, it is possible for a heat flow which is introduced into the valve plate to be dissipated via the projecting region, with the result that an input of heat into the inlet chamber and into the compression space housing and to the components of the compressor which are contained therein is reduced.

In a next advantageous refinement of the compressor, the projecting region of the cooling fan is configured to act as a cooling fin.

In the case of the action as a cooling fin, the heat which is introduced into the valve plate is emitted via the projecting region, with the result that it is not introduced into the compression space housing.

In the case of further advantageous refinements of the compressor, a cross-sectional area of the inlet chamber, as the heat flow reduction device, in a region of the inlet valve corresponds approximately to a cross-sectional area of a component of the inlet valve in the inlet chamber, and/or a cross-sectional area of the outlet chamber in a region of the outlet valve corresponds approximately to a cross-sectional area of a component of the outlet valve in the outlet chamber.

As a result of this property, a contact area of the gas to be sucked in in the inlet chamber with the inlet chamber wall is reduced, and/or a contact area of the gas to be ejected in the outlet chamber with the outlet chamber wall is reduced, with the result that a heat flow between them is reduced.

In accordance with a further advantageous refinement of the compressor, a cross-sectional area of a portion, axially adjoining the inlet opening, of the inlet chamber corresponds, as the heat flow reduction device, approximately to a cross-sectional area of the inlet opening, and/or a cross-sectional area of a portion, axially adjoining the outlet opening, of the outlet chamber corresponds, as the heat flow reduction device, approximately to a cross-sectional area of the outlet opening.

As a result of this property, a contact area of the gas to be sucked in in the inlet chamber with the inlet chamber wall is reduced, and/or a contact area of the gas to be ejected in the outlet chamber with the outlet chamber wall is reduced, with the result that a heat flow between them is reduced.

In accordance with a further disclosed embodiment, a vehicle compressed air system comprises a compressor explained above.

FIG. 1 diagrammatically shows a vehicle compressed air system 1 with a compressor 2 for providing compressed air for the vehicle compressed air system in a sectional illustration with a connector portion 3 and a part of a compression space housing 4. Furthermore, the vehicle compressed air system 1 has components (not shown) such as, for instance, an air preparation unit, lines, valves, etc.

The connector portion 3, usually a cylinder head in the case of reciprocating compressors, has an inlet chamber 5 with an inlet opening 6 for sucked-in air and an outlet chamber 7 with an outlet opening 8 for air which is compressed by way of the compressor 2. The inlet chamber 5 is formed by way of an inlet chamber wall 5′, and the outlet chamber 7 is formed by way of an outlet chamber wall 7′. In alternative embodiments, the compressor 2 is not constructed as a reciprocating compressor, but rather with a different functional principle, for example in accordance with a screw compressor.

Furthermore, the compressor 2 has a valve plate 9 with an inlet valve 10 and an outlet valve 11. The valve plate 9 is introduced between the connector portion 3 and the compression space housing 4, and is clamped in between by screws (not shown), by way of which the connector portion 3 and the compression space housing 4 are connected to one another, and seals both the inlet chamber 5, the outlet chamber 7 and a compression space in the compression space housing 4. The valve plate 9 is defined as the inlet chamber wall 5′ in a portion on the side of the inlet chamber 5, and is defined as the outlet chamber wall 7′ in a portion on the side of the outlet chamber 7. In alternative embodiments, no separate valve plate 9 is provided, but rather the inlet valve 10 and the outlet valve 11 are contained in each case in a wall of the connector portion 3, namely in the inlet chamber wall 5′ and the outlet chamber wall 7′. In further alternative embodiments, the valve plate 9 can also have a different number of inlet valves 10 and outlet valves 11, or either only at least one inlet valve 10 or only at least one outlet valve 11 is provided.

Furthermore, FIG. 1 diagrammatically shows heat flows which occur in the compressor 2. “I” denotes a heat flow from a hot gas side, namely from the outlet chamber 7, via the cylinder head, namely the outlet chamber wall 7′ and the inlet chamber wall 5′ which are shown here configured integrally, to a cold gas side, namely to the inlet chamber 5. “II” denotes a heat flow from the hot gas side, namely from the outlet chamber 7, via the valve plate 9 to the cold gas side, namely to the inlet chamber 5. “III” denotes a heat flow from the hot gas side, namely the connector portion 3, to the compression space housing 4 and to further components, for example a piston (not shown) and via a crankcase (not shown) to a crank drive (not shown).

FIG. 2 shows a first embodiment of a compressor 2. The compressor 2 has a heat flow reduction device which is configured to reduce at least one of a heat flow I from a component of the compressor 2 which is connected to the inlet chamber wall 5′, here, the outlet chamber wall 7′, to the sucked-in air in the inlet chamber 5 and a heat flow I from the compressed air in the outlet chamber 7 to a component of the compressor 2 which is connected to the outlet chamber wall 7′, here, the inlet chamber wall 5′.

To this end, the heat flow reduction device in the first embodiment of the compressor 2 has an inlet chamber wall 5′ and an outlet chamber wall 7′ which have two surfaces 12, 13 which lie opposite one another. Between the two surfaces 12, 13 which lie opposite one another, a first air gap 14 of the heat flow reduction device is formed by way of the outlet chamber wall 7′ and the inlet chamber wall 5′ as constituent part of the heat flow reduction device.

The inlet chamber wall 5′ and the outlet chamber wall 7′ are formed as separate components in this embodiment.

In one variant (shown in FIG. 3) of the first embodiment of the compressor 2, the inlet chamber wall 5′ and the outlet chamber wall 7′ are formed integrally or have a portion which connects them, the first air gap 14 separating or spacing apart a remaining part of the inlet chamber wall 5′ and the outlet chamber wall 7′ from one another.

FIG. 4 shows a second embodiment of the compressor 2. Here too, the compressor 2 has the connector portion 3 with the inlet chamber 5 and the outlet chamber 7, and the compression space housing 4 which is configured such that the air which is sucked in is compressed therein. Furthermore, the compressor 2 has the valve plate 9 between the connector portion 3 and the compression space housing 4, with the result that the valve plate 9 forms a portion of the inlet chamber wall 5′ and also of the outlet chamber wall 7′.

Furthermore, this embodiment has, as the heat flow reduction device, a first thermal insulation material 15 between the inlet chamber wall 5′ and the outlet chamber wall 7′ on one side and the valve plate 9 on the other side. In alternative embodiments, the first thermal insulation material 15 can also be provided only either between the inlet chamber wall 5′ and the valve plate 9 or between the outlet chamber wall 7′ and the valve plate 9.

FIG. 5 shows a third embodiment of the compressor 2. In this embodiment, a first contact surface 16 is formed in each case between the connector portion 3 and the valve plate 9 by way of the inlet chamber wall 5′ and the outlet chamber wall 7′, which first contact surface 16 is in contact with the valve plate 9. In the direction of a continuation of a surface of the valve plate 9 which forms the first contact surface 16, a second air gap 17 is provided next to the respective contact surface 16, which second air gap 17 is formed by way of a first cutout in the inlet chamber wall 5′ and the outlet chamber wall 7′. By way of the first cutout as the heat flow reduction device, the first contact surface 16 is decreased in comparison with a cross-sectional area of the inlet chamber wall 5′ and the outlet chamber wall 7′ following the first cutout away from the valve plate 9. The inlet chamber wall 5′ and the outlet chamber wall 7′ and the valve plate 9 seal the inlet chamber 5 and the outlet chamber 7 with the first contact surface 16 next to the second air gap 17. In alternative embodiments, the second air gap 17 can be formed either only between the inlet chamber wall 5′ and the valve plate 9 or the outlet chamber wall 7′ and the valve plate 9. In a further alternative embodiment, the first cutout is not provided exclusively in the inlet chamber wall 5′ and the outlet chamber wall 7′, but rather instead or in addition in the valve plate 9.

FIG. 6 shows a fourth embodiment of the compressor 2. In this embodiment, a second thermal insulation material 18 is provided between the valve plate 9 and the compression space housing 4. The second thermal insulation material 18 is provided on contact surfaces of the compression space housing 4 and the valve plate 9. In embodiments, in which no separate valve plate 9 which is defined as the inlet chamber wall 5′ and the outlet chamber wall 7′ is provided, the second thermal insulation material is introduced between the inlet chamber wall 5′ and the outlet chamber wall 7′ on one side and the compression space housing 4 on the other side. In further alternative embodiments, the second thermal insulation material is provided either only between the inlet chamber wall 5′ and the compression space housing 4 or between the outlet chamber wall 7′ and the compression space housing 4.

FIG. 7 shows a fifth embodiment of the compressor 2. In this embodiment, a second contact surface 19 is formed between the valve plate 9 and the compression space housing 4 by way of the valve plate 9 which is defined as inlet chamber wall 5′ and outlet chamber wall 7′ and a wall of the compression space housing 4. In the direction of a continuation of a surface of the valve plate 9 which forms the second contact surface 19, a third air gap 20 is provided next to the contact surface 19, which third air gap 20 is formed by way of a second cutout in the wall of the compression space housing 4. By way of the second cutout as the heat flow reduction device, the second contact surface 19 is reduced in comparison with a cross-sectional area of the wall of the compression space housing 4 following the second cutout away from the valve plate 9. The compression space housing 4 and the valve plate 9 seal the compression space with the second contact surface 19 next to the third air gap 20. In alternative embodiments, the third air gap 20 can be formed either only between the inlet chamber wall 5′ and the compression space housing 4 or between the outlet chamber wall 7′ and the compression space housing 4. In a further alternative embodiment, the second cutout is not provided exclusively in the compression space housing 4, but rather instead or in addition in the valve plate 9 which is defined as inlet chamber wall 5′ and outlet chamber wall 7′. In a further alternative embodiment, the valve plate 9 is not present, but rather the cutout is or the cutouts are provided in the inlet chamber wall 5′ and/or the outlet chamber wall 7′.

FIG. 8 shows a sixth embodiment of the compressor 2. Here, the valve plate 9 has a projecting region 21 as the heat flow reduction device which projects outward from the connector portion 3 and the compression space housing 4 and is configured to act as a cooling rib.

In alternative embodiments, the valve plate 9 does not have to project on both sides, as shown, but rather can also have regions 21 which project only in portions.

Here, the projecting regions 21 as the heat flow reduction device bring about that heat is emitted from the valve plate 9 into the surrounding area, with the result that the heat flow from a component which is connected to the inlet chamber wall 5′ to the sucked-in air in the inlet chamber 5 and the heat flow from the compressed air in the outlet chamber 7 to the part which is connected to the outlet chamber wall 7′ are reduced.

FIG. 9 shows a seventh embodiment of the compressor 2. In this embodiment, the heat flow reduction device is provided such that a surface of the inlet chamber wall 5′ and/or a surface of the outlet chamber wall 7′ which are in contact with the compressed hot air or with the sucked-in cold air are or is minimized, in order to reduce the heat flow.

To this end, as shown in FIG. 9, a cross-sectional area of the inlet chamber 5 parallel to a surface of the valve plate 9 which faces the connector portion 3 in a region of the inlet valve 10 corresponds approximately to a cross-sectional area of a component of the inlet valve 10 in the inlet chamber 5. Furthermore, a cross-sectional area of the outlet chamber 7 parallel to a surface of the valve plate 9 which faces the connector portion 3 in a region of the outlet valve 11 corresponds approximately to a cross-sectional area of a component of the outlet valve 11 in the outlet chamber 7. The property that the cross-sectional area of the inlet chamber 5 and the outlet chamber 7 in the region of the inlet valve 10 and the outlet valve 11, respectively, corresponds approximately to the cross-sectional area of the inlet valve 10 and the outlet valve 11, respectively, means that the cross-sectional areas of the inlet chamber 5 and the outlet chamber 7 correspond at least to a cross-sectional area of that component of the inlet valve 10 and the outlet valve 11, respectively, provided in the inlet chamber 5 and the outlet chamber 7, or else can be slightly greater, in order to make a flow of the air out of the inlet chamber 5 or into the outlet chamber 7 without disruptions possible. In alternative embodiments, only one of the cross-sectional areas in the region of the respective valve 10, 11 corresponds approximately to the cross-sectional area of the component of the respective valve 10, 11. In the alternative embodiments, in which no valve plate 9 is provided, the respective cross-sectional area is parallel to the inlet chamber wall 5′ and/or the outlet chamber wall 7′ of the connector portion 3, in which the inlet valve 10 and the outlet valve 11, respectively, are provided.

Furthermore, as shown in FIG. 9, a portion of the inlet chamber 5 which axially adjoins the inlet opening 6 has a cross section which corresponds approximately to a cross section of the inlet opening 6, and a portion of the outlet chamber 7 which axially adjoins the outlet opening 8 has a cross section which corresponds approximately to a cross section of the outlet opening 8. The property that the cross-sectional area of a portion of the inlet chamber 5 and the outlet chamber 7, respectively, which axially adjoins the inlet opening 6 and the outlet opening 8 corresponds approximately to the cross-sectional area of the inlet opening 6 and the outlet opening 8, respectively, means that the cross-sectional area of the adjoining portion corresponds at least to the cross-sectional area of the inlet opening 6 and the outlet opening 8, respectively, or is as small as possible but so much greater that an inflow of the air into the inlet chamber 5 and an outflowing air from the outlet chamber 7 is just possible without disruptions. In alternative embodiments, only one of the axially adjoining cross-sectional areas corresponds approximately to the cross-sectional area of the respective opening 6, 8.

All the features which are shown in the description, the following claims and the drawing can be essential to the disclosed embodiments both individually and in any desired combination with one another; in particular, a combination of all the embodiments is possible.

LIST OF DESIGNATIONS

• • 1 Vehicle compressed air system
  • 2 Compressor
  • 3 Contact portion
  • 4 Compression space housing
  • 5 Inlet chamber
  • 5′ Inlet chamber wall
  • 6 Inlet opening
  • 7 Outlet chamber
  • 7′ Outlet chamber wall
  • 8 Outlet opening
  • 9 Valve plate
  • 10 Inlet valve
  • 11 Outlet valve
  • 12, 13 Surfaces
  • 14 First air gap
  • 15 First thermal insulation material
  • 16 First contact surface
  • 17 Second air gap
  • 18 Second thermal insulation material
  • 19 Second contact surface
  • 20 Third air gap
  • 21 Projecting region

Claims

1. A compressor for providing compressed air for a vehicle compressed air system, the compressor comprising: an inlet chamber formed by an inlet chamber wall and provided with an inlet opening for sucked-in air;an outlet chamber formed by an outlet chamber wall and provided with an outlet opening for air compressed by the compressor; anda heat flow reduction device configured to reduce at least one of a heat flow from a component of the compressor connected to the inlet chamber wall to the sucked-in air in the inlet chamber and a heat flow from the compressed air in the outlet chamber to a component of the compressor connected to the outlet chamber wall.

2. The compressor of claim 1, wherein the heat flow reduction device has at least parts of the inlet chamber wall and the outlet chamber wall configured such that a first air gap is configured between two opposite surfaces of the outlet chamber wall and the inlet chamber wall.

3. The compressor of claim 2, wherein the inlet chamber wall and the outlet chamber wall are configured as separate components.

4. The compressor of claim 2, wherein the inlet chamber wall and the outlet chamber wall are formed integrally, and the first air gap is configured such a way that the inlet chamber wall and the outlet chamber wall are spaced apart from one another at least partially.

5. The compressor of claim 1, further comprising: a connector portion for the inlet chamber and the outlet chamber,a compression space housing configured such that the sucked-in air is compressed therein, anda valve plate between the connector portion and the compression space housing,wherein the valve plate forms a portion of the inlet chamber wall and the outlet chamber wall, andwherein the heat flow reduction device has a first thermal insulation material at least between one of the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side.

6. The compressor of claim 5, wherein the first thermal insulation material is provided between both the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side.

7. The compressor of claim 2, further comprising: a connector portion for the inlet chamber and the outlet chamber,a compression space housing configured such that the sucked-in air is compressed therein, anda valve plate between the connector portion and the compression space housing, anda first contact surface being formed between the inlet chamber wall and the outlet chamber wall on one side and the valve plate on the other side,wherein the heat flow reduction device having a first cutout in at least one of the inlet chamber wall, the outlet chamber wall and the valve plate next to the first contact surface, such that the first cutout is configured to form a second air gap next to the first contact surface.

8. The compressor of claim 1, the compressor having a compression space housing which is configured such that the sucked-in air is compressed therein, andthe heat flow reduction device having a second thermal insulation material between at least one of the inlet chamber wall and the outlet chamber wall on one side and the compression space housing on the other side.

9. The compressor of claim 7, further comprising: a compression space housing configured such that the sucked-in air is compressed therein, anda second contact surface being formed between the compression space housing on one side and the inlet chamber wall and the outlet chamber wall on the other side,wherein the heat flow reduction device has, in at least one of the inlet chamber wall, the outlet chamber wall and the compression space housing, next to the second contact surface, a second cutout which is configured such that a third air gap is formed next to the second contact surface.

10. The compressor of claim 1, further comprising: a connector portion for the inlet chamber and the outlet chamber,a compression space housing configured such that the sucked-in air is compressed therein, anda valve plate between the connector portion and the compression space housing,wherein, as the heat flow reduction device, the valve plate has a region which projects from the connector portion and the compression space housing.

11. The compressor of claim 10, wherein the region which projects from the compression space housing is configured to act as a cooling fin.

12. The compressor of claim 1, wherein a cross-sectional area of the inlet chamber in a region of the inlet valve corresponding approximately to a cross-sectional area of a component of the inlet valve in the inlet chamber is configured as the heat flow reduction device.

13. The compressor of claim 1, wherein a cross-sectional area of the outlet chamber in a region of the outlet valve corresponding approximately to a cross-sectional area of a component of the outlet valve in the outlet chamber is configured as the heat flow reduction device.

14. The compressor of claim 1, further comprising a portion, axially adjoining the inlet opening, of the inlet chamber, wherein a cross-sectional area which corresponds approximately to a cross-sectional area of the inlet opening is configured as the heat flow reduction device.

15. The compressor of claim 1, further comprising a portion, axially adjoining the outlet opening, of the outlet chamber, wherein a cross-sectional area which corresponds approximately to a cross-sectional area of the outlet opening is configured as the heat flow reduction device.

16. A vehicle compressed air system with a compressor as claimed in claim 1.