EP3615800A1

EP3615800A1 - Compressor, compressed air supply facility for operating a pneumatic system, and method for operating a compressed air supply facility

Info

Publication number: EP3615800A1
Application number: EP18716597.2A
Authority: EP
Inventors: Jonas Wichern; Klaus Bredbeck; Uwe Stabenow
Original assignee: Wabco GmbH
Current assignee: ZF CV Systems Europe BV
Priority date: 2017-04-28
Filing date: 2018-04-06
Publication date: 2020-03-04
Anticipated expiration: 2038-04-06
Also published as: US20200102947A1; CN110892156B; US11168679B2; EP3615800B1; CN110892156A; WO2018197182A1; DE102017004088A1

Abstract

The invention relates to a compressor, particularly a compressor for a compressed air supply of a compressed air supply facility, for operating a pneumatic system, comprising a first compression chamber, a second compression chamber, an air supply connection and a compressed air outlet, and a piston, the piston being connected to a drive by means of a connecting rod, and a first compression chamber and a second compression chamber being interconnected by means of a connection line. According to the invention, the connecting rod is rigidly connected to the piston, on a piston side, in a particularly rigid and joint-free manner, and is connected to a rotating part of the drive, on a drive side, in a rotatably movable manner, and the piston has at least one seal on the stage side, for sealing the first compression chamber and/or the second compression chamber.

Description

Compressor, compressed air supply system for operating a pneumatic system and method for operating a compressed air supply system

The invention relates to a compressor, in particular a compressor, for a compressed air supply of a compressed air supply system, for operating a pneumatic system according to the preamble of claim 1. The invention further relates to a compressed air supply system for operating a pneumatic system, a method for operating a compressed air supply system and a vehicle with a compressed air supply system.

Compressors, in particular piston compressors in vehicles of all kinds, are commonly known. They serve to provide compressed air and include many areas of application, including brake systems, air suspension systems, in particular for level control, clutch amplifiers and many more.

Important target criteria in the design of compressors include the highest possible delivery rate, the lowest possible noise, the smallest possible dimensions, low production costs and a high level of robustness.

DE 10 2012 019 618 A1 discloses a production method for a piston with a circumferential seal in the form of a circular cup sleeve, in particular for use in a reciprocating piston compressor.

In DE 10 201 1 121 750 A1, for example, a compressor is disclosed, comprising a piston whose piston head is rigidly connected to a connecting rod, wherein a connecting rod bearing eye of the connecting rod is rotatably mounted on an eccentric pin of a drive shaft of a drive motor. Nevertheless, the approach of the rigid connection between the connecting rod and the piston due to the structurally related wobbling leads to leaks between the piston and cylinder, which should be countered by appropriate design measures, such as seals.

DE 10 2013 101 1 10 A1 discloses a reciprocating compressor with a driven by a sliding crank and a reciprocable in a cylinder and against the cylinder wall sealed piston, which is arranged fixed to the connecting rod, wherein the piston and / or the cylinder is formed are that during the compression stroke caused by the relative inclination or tilt between the piston and cylinder crescent-shaped gaps between the piston edge and the cylinder wall are sealable, thereby compensating for leaks.

The concept of a two-stage compressor, in which the supplied air is first compressed to a low-pressure level in a low-pressure stage and then to a high-pressure level in a high-pressure stage connected to the low-pressure stage, has proven successful.

To increase the compactness, a two-stage compressor can be designed in such a way that both compressor stages are formed by only one piston, for example by means of a double-sided piston.

For example, GB 241, 907 discloses a multi-stage compressor which can realize any number of compressor stages by means of a piston having any number of step sections and a cylinder adapted to it.

Furthermore, DE 10 2010 054 710 A1 discloses a compressor for a compressed air supply of a compressed air supply system, which has at least one two-stage compressor unit with a single cylinder a single in a compression chamber of the cylinder can be acted upon on two sides piston.

DE 10 2012 223 1 14 A1 furthermore describes a double-piston compressor unit. A drive shaft of the motor of the compressor unit acts via a slotted guide in the double piston of the unit with this together so that the double piston performs alternately in the two cylinders of the unit a compression process. Here, the axis of the drive shaft is arranged eccentrically to the central axis of the two cylinders, resulting in fewer changes in position of the piston and thus a lower noise.

The concept is still in need of improvement with regard to the above-mentioned disadvantages and target criteria. It is therefore desirable to realize the function of an efficient, in particular two-stage, compressor in the most compact and robust design possible.

At this point, the invention begins, whose task is to provide a compressor in an improved manner, which at least partially meets the objectives and target criteria formulated above, in particular by a simplified structural design.

The task concerning the compressor is achieved with a compressor of claim 1.

The invention relates to a compressor, in particular a compressor, for a compressed air supply of a compressed air supply system, for operating a pneumatic system, comprising:

a first compression space, a second compression space, an air supply port and a compressed air outlet, and

a piston having a first pressurisable end face, which is directed towards the first compression space, and a second pressurisable end face, which is opposite the first end face, and which is directed towards the second compression space, wherein the first compression chamber is delimited by the first end face and the second compression space is bounded by the second end face of the piston, wherein the first end face is a full side and the second end face is a step side, and

- The piston is connected via a connecting rod to a drive, and wherein the first compression chamber and the second compression chamber are connected to each other via a connecting line.

According to the invention, it is provided that the connecting rod is rigid, in particular rigid and joint-free, connected to the piston on a piston side and is rotatably connected to a drive side with a rotating part of the drive, and the piston carries at least one seal on the step side, which the first Compressing space and / or the second compression chamber seals.

Preferably, the connecting rod can be rigidly connected in the sense of rigid and joint-free on a piston side with the piston. One approach to constructive simplification of the compressor is the rigid connection of the connecting rod and piston and the associated acceptance of a certain wobbling movement of the piston during the stroke.

Such compressors, also known as wobble piston compressors or reciprocating piston compressors, lead to the advantage that less moving parts have to be used to couple drive and piston and, if necessary, no guide elements are required for the piston for receiving lateral forces introduced by the connecting rod.

The invention is based on the consideration that single-stage wobble piston compressors have advantages in terms of their simple structural design. These include in particular a lower susceptibility to errors, a smaller number of parts and assemblies, as well as easier maintenance and repair. At the same time, however, there are design-related problems, which in particular are due to the tumbling motion, ie the relative ve inclination between the piston axis and cylinder axis depending on the stroke, are due. These problems, in particular the not purely translational stroke movement of the piston, is encountered in the prior art with design measures, in particular suitable seals.

Furthermore, the invention is based on the consideration that a two-stage compressor with only both a single piston and a single cylinder leads to significant advantages in terms of the reduction of parts, in particular moving parts, and thus to a more compact design of the compressor. At the same time, there are also challenges in this compressor concept, including, in particular, the absorption of lateral forces, in order to ensure the translatory lifting movement of the piston, which can be pressurized on both sides, and thus, above all, the sealing of both compression chambers separated from the piston. Through the use of suitable guides and bearings, a purely translational lifting movement of the piston or of the piston rod, which is driven in particular by a crankshaft, can be ensured.

The invention has surprisingly recognized that the combination of these two supposedly contradictory compressor concepts, namely that of the wobble piston compressor and that of the two-stage, einkolbigen compressor is possible and leads to the above already mentioned, significant advantages of both approaches. Contrary to the widely held in the prior art view that the sealing of both compression chambers can be ensured in a two-stage, einkolbigen compressor only in a purely translational lifting movement, the invention is based on the consideration that the design-related wobbling movement with appropriate design measures, in particular seals, can be countered. In this case, the invention has recognized, in particular, that in the case of a corresponding, in particular cylindrical or annular, cylindrical formation of the first and second compression space, in particular together with a piston which can be pressurized on both sides, only one seal can be used. Further developments of the invention are specified in the dependent claims, which further develop the invention within the scope of the task with regard to further advantages.

In particular, it is provided that the piston has a non-return valve opening from the first compression chamber in the direction of the air supply port against a spring force.

Concretely, this check valve can be arranged in an opening on the full side and thus between the first compression space and the air supply connection or the air inlet region open to the environment. By environment is meant in particular the lower-pressure crankcase interior. In particular, can be achieved by a gas-conducting connection from the crankcase interior, in particular an opening, line, valve and / or the like, between the crankcase interior and a location outside of the crankcase location, that the crankcase interior is practically below ambient pressure, that is under pressure the atmosphere surrounding the crankcase, and especially the vehicle.

The check valve can thus open automatically in the event of a pressure above the normal level in the first compression chamber, in particular to avoid damage.

Furthermore, the integration of the check valve in the piston leads to the advantage that the valve can be replaced together with the piston, or disassembled and / or repaired. Overall, the invention has recognized that an integration of the movable and / or wear-prone parts of the compressor in the piston, in particular valve flap pen, check valves and seals, leading to the advantageous effect of simplified accessibility and / or interchangeability.

In a preferred embodiment, it is provided that the connecting rod is rotatably connected to the rotating part of the drive in the form of an eccentrically arranged shaft portion. In this way, the rotational movement of the drive is converted into a predominantly translational motion components having wobbling motion.

It is advantageously provided that the connecting rod is integrally formed and articulated against the piston. This includes the rigid connection between the piston and connecting rod, especially without relative inclinations balancing joints. In this way, the construction and the production of the compressor are simplified and the number of moving parts is reduced. This in turn leads advantageously to a reduced susceptibility to errors and reduced repair and maintenance costs.

In particular, it is provided that the first compression chamber is cylindrical or cylindrical with a dome-shaped section and the second compression chamber is annularly cylindrical.

Concretely, this embodiment can be formed by an inside cylinder-shaped, rotatable cylinder inner web having an L-shaped cross-section, which is open in the direction of the piston and thus forms an annular cylindrical compression space. The term "annularly cylindrical" here describes a compression space which, in contrast to the first compression space, is not fully cylindrical but hollow cylindrical, ie has an inner cylindrical outer surface and an outer cylindrical outer surface Compaction space for generating the compression oscillating moves. This annular shape of the compression chamber leads to the advantage that it can be sealed by only one, in particular piston side mounted seal. Also, this annular shape of the compression chamber avoids, in contrast to other, belonging to the prior art approaches of two-stage, einkolbigen compressors that further moving parts, in particular connecting rod or piston rod, directly adjacent to the compression space and thus would have to be additionally sealed.

Furthermore, a piston shape can be achieved by a dome-shaped section or generally tapering towards the full side of the piston, which advantageously does not tilt in the cylinder despite wobbling motion.

Within the scope of a preferred development, it is provided that the at least one seal of the piston effects a pressure-tight seal acting in the radial direction both on an outer side and on an inner side, in particular as a single seal. Here, the single seal may be formed, for example, as a boot seal.

In such a configuration, the sealing of both the compaction spaces with each other and the compaction spaces of the environment, with only one seal which seals in the radial direction on both sides, that is, both inwardly and outwardly, takes place. This development leads to the advantage that the construction of the compressor is simplified by the use of a few seals, in particular only a single seal for sealing the annular compression space, in particular both compression chambers, and thus costs are reduced and the number of parts, in particular wear-prone parts , is reduced. Also, the arrangement of the seal on the step side of the piston to a simple manufacture or assembly of piston and seal. In a preferred embodiment, it is provided that the seal for sealing the second compression chamber is formed against a crankcase interior and for sealing the first compression chamber against the second compression chamber.

It is advantageously provided that the outside of the seal circumferentially in contact with a cylinder inner wall and the inside of the seal is circumferentially in contact with a web wall inside. Specifically, this may include the seal having an outside and an inside. The outside of the seal is on the outer circumference, ie the outside of the - simplified described - arranged annular seal and thus provides a circumferential, continuous contact with a, in particular a cylindrical cavity-forming cylinder inner wall ago. The inside of the seal is on the inside, ie on the inner circumference of the - simplified described - arranged annular seal and thus creates a circumferential, continuous contact with a web wall inside.

As part of a further development, it is provided that the seal has an annular sealing body with a first annular lip radially outward on the annular body and a second annular lip radially inward on the annular body.

As part of a further development, it is provided that the seal has an annular sealing body with a first annular lip, which is arranged in the radial direction on the outside of the sealing body, directed in the axial direction to the second compression chamber, and / or a second annular lip, the inside in the radial direction on the sealing body, directed in the axial direction to the second compression space, is arranged. The first and / or second annular lip in particular has a free end which is arranged in the second compression space.

Such a development includes in particular that between the first annular lip and a main body of the seal body, a first Expansion space is formed, and between the second annular lip and the main body, a second expansion space.

Due to the first and second expansion space, compressed air located in the second compression space causes both the first annular lip and the second annular lip to press against the cylinder inner wall, thus causing a seal. Here, a first seal between the first annular lip and a wall outside of the cylinder inner wall, and a second seal between the second annular lip and a wall inside of the cylinder inner wall is effected.

A development with such a sealing body can be used in particular when a compressor is used in two-stage operation. A two-stage operation includes in particular that the compressed air is first in the first compression chamber to a lower pressure, for example, 3 bar, compressed and then compressed in the second compression chamber to a higher pressure, for example 22 bar. In such an operating mode, the first pressure in the first compression chamber, for example, assumes a value of max. 3 bar, and the second pressure in the second compression chamber, for example, a value between 3 bar and 22 bar.

As part of a further development, it is provided that the annular sealing body has a third annular lip, which is arranged in the radial direction on the outside of the sealing body, directed in the axial direction to the first compression space. The third annular lip in particular has a free end, which is arranged in the first compression space.

In such a development is advantageous, in particular by a third expansion space, a third seal between the third annular lip and the wall outer side of the cylinder inner wall causes. The third seal advantageously ensures that a seal between the first compression chamber and the second compression chamber is independent of the conditions prevailing in the first and second compression chambers. the pressures occur. In particular, when the first pressure prevailing in the first compression chamber is equal to or greater than the second pressure prevailing in the second compression chamber, an overflow of compressed air from the first compression chamber into the second compression chamber is prevented by the third annular lip. As a result, a single-stage operation of the compressor is advantageously made possible, is compressed in the compressed air in the first compression chamber and in the second compression chamber to the same final pressure. In such an operating mode, compressed air is compressed to the same final pressure of, for example, 18 bar in both compression chambers. Thus, in such an example, both the first pressure in the first compression space and the second pressure in the second compression space take a value of max. 18 bar.

In the context of a preferred development it is provided that the piston has a non-cylindrical outer cross-section that is variable in the axial direction. Specifically, this means, for example, that the outer cross-section of the piston at the top and bottom of the piston is elliptical and round at a location between the upper and the lower end of the piston, d. H. the piston outer wall is not cylindrical.

It is advantageously provided that the piston has a non-cylindrical inner cross-section which is variable in the axial direction. Specifically, this may mean that the inner cross-section at the top and bottom of a piston forming the annular portion of the piston is elliptical and round at a location between the upper and lower end of the piston stage, d. H. the piston inner wall is not cylindrical.

Both of the above-mentioned developments lead to a uniform and independent of the wobbling motion and thus relative inclination between the cylinder and piston sealing the compression chambers. The variable shape of the piston outer wall ensures that provided that the outer cross section of the piston in a plane perpendicular to the axis of the cylinder plane remains virtually invariable at each stroke position, in particular congruent with the cylinder inner cross-section. The same aspect applies analogously to the piston inner wall with regard to the seal against the rotationally shaped cylinder inner web having an L-shaped cross section forming the second compression chamber.

Furthermore, such a development in a further embodiment, in particular with a seal, which simultaneously forms the largest outer cross section and the smallest inner cross section of the piston, be advantageously achieved, that the piston only via the seal in contact with the inner wall or the web wall of the cylinder stands. In this way, it is advantageously achieved that a low-friction sealing of the compression spaces with each other or against the environment is achieved by this virtually only linear contact in only a narrow axial region of the piston. In this way, also advantageously the risk of tilting of the piston in the cylinder, despite the tumbling motion, is reduced.

Within the scope of a preferred development, it is provided that the second compression chamber also has a charging connection for additionally supplying compressed air, in particular from a pressure medium reservoir. In this way, pre-compressed and stored air can be supplied to the second compression chamber as needed. Such a procedure allows the intermediate storage of compressed air to compress by means of the compressor in not fully utilized operating phases air in advance to a certain (intermediate) high pressure and retrieve this pre-compressed air at a later date, or further compress. In this way, the power of the compressor can be increased in the short term.

In particular, it is provided that the air supply connection is arranged inside the connecting rod and / or the piston. This training of Compressor leads, analogous to the development relating to the check valve integrated in the piston, in particular to an integration of components and functional features in an easily accessible or exchangeable component, in this case the piston, and thus to advantages in particular in terms of increased modularity through the use of standardized components and reduced maintenance and repair costs.

Advantageously, it is provided that the rotatable connection between connecting rod and eccentrically arranged shaft portion by means of a connecting rod bearing, in particular a plain bearing, ball bearing or needle bearing, is formed. Particularly advantageous is a low-maintenance, particularly preferably maintenance-free, design of the rotatable connection. This can be achieved for example by the use of plain bearings.

The invention leads to the solution of the problem also to a compressed air supply system with an aforementioned compressor and a method for operating a compressed air supply system.

The compressed air supply system is designed to operate a pneumatic system and has: an air supply and connected thereto via an air supply port compressor according to the invention, a pneumatically connected to the compressor via a compressed air outlet to the compressor having an air dryer main pneumatic line to a compressed air port of a gallery, one on a Charging port pneumatically connected to the compressor pressure fluid reservoir.

According to the invention, the compressor is designed according to the invention. The operation of the pneumatic system is designed in particular for the supply of compressed air consumers in a vehicle, in particular for the supply of air spring systems.

The invention leads to the solution of the problem also to a method with an aforementioned compressor for operating a compressed air supply system and a method for operating a compressed air supply system and a vehicle with a compressed air supply system. The method for operating a compressed air supply system comprises the steps of compressing air from a crankcase interior and / or the environment in a first compression chamber of the compressor to a low pressure level, further compressing the compressed in the first compression chamber of the compressed air to a low pressure level in a second compression chamber of the compressor to a high pressure level, and supplying compressed in the second compression chamber to a high pressure level compressed air from the compressed air outlet via a pneumatic main to a compressed air port of a gallery, in particular via an air dryer. In the method, the advantages of the compressor are used advantageously. In the vehicle and in the compressed air supply system, the advantages in particular the advantages of the compressor according to the concept of the invention can also be used advantageously. These include in particular the compact design, which results from a two-stage, einkolbigen Taumelkolbenkompressor according to the concept of the invention and in particular leads to an advantageous for vehicles space and weight reduction.

Embodiments of the invention will now be described below with reference to the drawing. This is not necessarily to scale the embodiments, but the drawing, where appropriate for explanation, executed in a schematized and / or slightly distorted form. With regard to additions to the teachings directly recognizable from the drawing reference is made to the relevant prior art. It should be noted that manifold modifications and changes can be made in the form and detail of an embodiment without departing from the general idea of the invention.

The disclosed in the description, in the drawing and in the claims features of the invention may be essential both individually and in any combination for the development of the invention. In addition, all combinations of at least two of the features disclosed in the description, the drawings and / or the claims fall within the scope of the invention. The general idea of the invention is not limited to the exact form or detail of the preferred embodiments shown and described below, or limited to an object that would be limited in comparison with the subject matter claimed in the claims. For the given design ranges, values within the stated limits should also be disclosed as limit values and be arbitrarily usable and claimable. For simplicity, the same reference numerals are used below for identical or similar parts or parts with identical or similar function.

Further advantages, features and details of the invention will become apparent from the following description of the preferred embodiments and from the drawing; this shows in:

1 is a pneumatic circuit diagram of a pneumatic system with a particularly preferred embodiment of a compressed air supply system,

2A is a schematic sectional view of a compressor according to an embodiment in a sectional plane perpendicular to the drive axis,

2B is a schematic sectional view of a compressor according to the embodiment in a sectional plane parallel to both the Antriebsais and the piston axis, 3 is a sectional view of a compressor according to another embodiment in the installed state,

4A shows a detailed view of a piston of a still further embodiment in a sectional plane perpendicular to the drive axle,

4B is a detail view of a piston of the still further embodiment in a sectional plane parallel to both the drive and the piston axis,

5A, B, a first embodiment of a seal for a compressor,

Fig. 5C, D, a first embodiment of a seal for a compressor.

Compressors according to the concept of the invention are preferably used in a compressed air supply system - here, special demands have been made in terms of compaction performance and compactness. However, a compressor according to the concept of the invention can be used for other types of compressed air sources. A compressed air supply system is shown by way of example as a preferred embodiment in Fig. 1 and described below.

However, it should be clear that the compressor according to the concept of the invention can not only be used preferably in compressed air supply systems or for the passenger car or commercial vehicle sector. There have also been applications for vacuum generators, in particular vacuum pumps.

1 shows a pneumatic system 300 with a compressed air supply system 200 and a pneumatic system 500 formed in the present case in the form of an air spring system of a vehicle 400 (not shown).

In the present case, the air spring system is formed with an exemplary number of four air springs 210, each air spring 210 a wheel not one associated vehicle 400 is assigned. From the vehicle 400, in the present case only symbolically a support 410 formed near the wheel is shown, which can be raised when the air spring 210 is filled or lowered when the air spring 210 is vented. An air spring 210 comprises an air bellows referred to here as a bellows 21 1 for receiving compressed air and an air spring valve 212 which holds or discharges the amount of compressed air in the bellows 21 1 or allows filling of the bellows 21 1 with compressed air.

The air spring valve 212 is formed as a controllable solenoid valve, here as a 2/2-way valve. Each of the air spring valves 212 is presently shown in a state in which the spring force of an unspecified spring in a normally closed state.

The air spring valves 212 are connected to a gallery line 220 designed as a manifold via suitable spring branch lines 221. Connected directly to the gallery line 220 is a voltage-pressure sensor 230 which is capable of measuring a pressure in the gallery line 220 - and, with suitable switching of the air spring valves 212 - also a pressure in the air springs 210. The voltage-pressure sensor 230 can also measure a storage pressure in conjunction with a storage system, namely the storage 224, the pneumatic line 40 and the storage valve 41 in the present case. Pressure sensor signals can be transmitted to initiate further control measures to an air spring control and / or a vehicle control, which is not shown here in detail. The supply of the pneumatic system 500 in the form of the air spring system takes place here with compressed air from the compressed air supply system 200th

The pneumatic system 500 is connected via a compressed air connection 2 to the compressed air supply system 200. The compressed air connection 2 compressed air can be supplied from a compressed air supply 10 with a compressor 100 via a pneumatic main line 30. The compressed air connection 2 can also compressed air from a pressure medium reservoir 224 via a further compressed air connection 2 'and a further pneumatic line 40 are supplied.

The compressed air supply system 200 has for appropriate selection of the type of supply of compressed air to the pneumatic system 500 suitable isolation valves, namely a first isolation valve 31 in the main pneumatic line 30 and a second isolation valve 41 in the further pneumatic line 40. The first and second isolation valve 31, 41 is in each case designed as a controllable solenoid valve - here as a 2/2-way valve.

1, the first and second isolation valves 31, 41 are each shown in a closed state, so that the pneumatic system 500 is completely separated from the compressed air supply system 200. This advantageously leads to an air dryer 222 of the compressed air supply system not being adversely affected (eg filled) by compressed air movements in the pneumatic system 500 or re-storage of compressed air from the pressure medium reservoir 224 into the pneumatic system 500 when the first isolation valve 31 is closed ,

Overall, the compressed air supply system 200 has a compressed air supply 10, to which the main pneumatic line 30 is connected. In the pneumatic main line 30 is compressed air supply side of the air dryer 222 and compressed air connection side, the first isolation valve 31 pneumatically connected in series. Between the air dryer 222 and the first isolation valve 31 is designed as a pneumatic parallel circuit valve assembly is connected.

The valve arrangement has a non-return valve 32 which automatically opens in the direction of ventilation B to the pneumatic system 500 and which blocks in the venting direction E from the pneumatic system 500 to the air dryer 222. In a direction parallel to the main pneumatic line 30 as a bypass line 33 connected pneumatic line, a throttle 34 is arranged, which serves as a regeneration throttle bidirectional flow. The throttle 34 has a nominal diameter which is sufficient to vent when venting Pneumatic system 500 with open first separating valve 31 to provide a pressure drop in such a way that an air dryer 222 sufficiently regenerated as part of a pressure swing adsorption.

A guided in the direction of vent E compressed air flow can be vented via a connected to the main pneumatic line 30 vent line 35 to a vent port 3 to the environment U. In the vent line 35 a to be opened for a venting further isolation valve 36 is arranged. The further isolation valve 36 is like the first and second isolation valve 31, 41 as a controllable solenoid valve, namely designed here as a 2/2-way valve.

In a modification not shown here, a fundamentally different design of the main pneumatic line 30 and vent line 35 may be provided, for. B. with a suitable pilot operated vent solenoid valve assembly or the like.

In the present case, the compressed air feed 10 has a compressor 100 designed according to the concept of the invention, which will be described below with reference to the particularly preferred embodiment shown by way of example in FIGS. 1, 2A and 2B. The compressor 100 of the compressed air supply 10 is formed with the compressed air supply 10 present as a separately connectable to the compressed air supply system 200 device. The insofar as compressed air supply device component to be designated the compressed air supply 10 has a compressed air outlet 124 to which the main pneumatic line 30 of the compressed air supply system 200 can be connected. Furthermore, the compressed air supply 10 has a charging connection 126, to which a pneumatic line 37 to the pressure medium reservoir 224 can be connected via a still further separating valve 38. To the pneumatic line 37 of the pressure medium reservoir 224 is connected via the above-mentioned second compressed air connection 2 '. To the second compressed air port 2 'and the other pneumatic line 40 is connected to the compressed air port 2. The pneumatic line 37 is - in the open even further isolation valve 38 - only unidirectionally flowed through by compressed air, namely in a pressure medium reservoir 224 looked, further venting direction E '. For this purpose, the pneumatic line 37 to another check valve 39, which opens automatically in the further venting direction E 'and locks in the opposite direction. The pneumatic line 37 is thus designed to supply compressed air from the pressure medium reservoir 224 to the charge port 126 of the compressed air supply 10 when the still further cutoff valve 38 opens.

Further, the compressed air supply 10 to an air supply port 0, can be supplied via the air from an air supply L - filtered in a filter 52 a suction 51.

As can be seen from FIG. 1, the compressor 100 of the compressed air supply 10 is designed with a first compression space 104 and a second compression space 106. According to the concept of the invention, in the embodiment described here, the compressor 100 is implemented with a single cylinder 1 18, as described in more detail in FIGS. 2A and 2B. A single piston 1 12 of the compressor 100, which can be pressurized on both sides in the interior of the cylinder 1 18, is driven by a motor M via a drive shaft 102 for movement. The cylinder 1 18 with piston 1 12 of the compressor 100 is presently arranged to form both compression spaces 104 and 106 on a single side of the motor M. As can be seen from the description of Fig. 2A and Fig. 2B, this is a particularly compact arrangement of the cylinder 1 18 using a single piston 1 12th

The compressed air supply or the compressor 100 has a connecting line 122 between the first compression chamber 104 and the second compression chamber 106.

The connecting line 122 is formed as a passage of a piston body of the piston 1 12 and is thus designed to be particularly compact. On- Because of the comparatively short connection line 122, the entire compression space in the cylinder 1 18 is kept low, so that a particularly high compression pressure amplitude can be achieved.

Optionally, the availability of compressed air, d. H. in particular an amount of compressed air, even further increase that on the second optional charging port 126 the second compression chamber 106 further pressure medium is supplied and - in a so-called boost operation - together with the compressed high level compressed air of the first compression chamber 104 in the second compression chamber 106th further compressed and made available in the compressed air outlet 124.

For such a compressor 100, various embodiments according to the concept of the invention are shown below, for which, in addition to the application shown in FIG. 1, further fields of use are conceivable.

FIG. 2A shows a compressor 100 according to a preferred embodiment in a first sectional view. Within a cylinder 1 18, a piston 1 12 12 is arranged in a cylindrical cavity. The piston 1 12 is rotatably connected via a rigidly connected connecting rod 128 via a rotatable connection 1 62 about a rotation axis extending through the point S2 perpendicular to the cutting plane with an eccentrically arranged shaft portion 132, which in turn is connected to a drive shaft 102 for transmitting the drive movement. Piston 1 12 and connecting rod 128 are present in one piece, in particular coaxially assembled along a common piston axis A executed. The piston 1 12 is still - as well as other areas of this view - shown very schematically. In particular, the formation of the piston 1 12 can - in particular for the realization of a function-related Taumelkinematik - of the training shown here differ. Such deviating developments are shown in FIGS. 3, 4A and 4B.

In the present case, the rotatable connection 1 62 is realized via a connecting rod bearing 152. The drive shaft 102 and the eccentrically arranged shaft portion 132 are part of a rotating part 131 of the drive. The connecting rod 128 has a piston side 128.1 facing the piston 12 and a drive side 128.2 facing the drive shaft 102.

The drive shaft 102, in turn, performs a rotational movement D about a rotational axis passing through a point S1 perpendicular to the cutting plane. Due to the rigid connection of the drive shaft 102 to the eccentrically arranged shaft portion 132 and the offset of the two points S1 and S2, a rotational movement of the drive shaft 102 leads to a deflection H of the piston in the stroke direction.

Furthermore, within the cylindrical cavity enclosed by the cylinder 18, a rotationally symmetrical cylinder inner web 110 extending radially inwardly from the cylinder inner wall 19 is arranged with an L-shaped cross section. The cylinder inner web 1 10 has due to the L-shaped cross-section on its inner side in the direction of the piston 1 12 directed web wall 1 1 1. Thus, an annular, in the direction of the piston 1 12 open space is formed by the inner wall of the cylinder 1 18 and the inner cylinder web 1 10, which is the second compression chamber 106.

The piston 1 12 has on the connecting rod 128 side facing away from a solid side 1 14 formed on the first end face 1 13, which limits the first compression space 104 together with the inner wall of the cylinder 1 18. Furthermore, the piston 1 12 on the connecting rod 128 side facing an annular piston step, which is in the form of a hollow cylinder whose outer wall is congruent with the outer wall of the piston 1 12 at the level of the full page 1 14 and which on the full page. 1 14 opposite side of the piston 1 12 by a as a step side 1 1 6 trained second end face 1 15 is completed.

Furthermore, the cylinder 1 12 is formed such that the piston 1 12, in particular the connecting rod 128 side facing the step side 1 1 6, oscillating within the cylinder inner web 1 10 and the inner wall of the cylinder 1 18 formed annular space can move. Due to the limitation of the cylinder inner web 1 10, inner wall of the cylinder 1 18 and step side 1 1 6 formed, practically annular space, the second compression chamber 106 is formed.

The piston 1 12 further has a seal 138, which is arranged in the illustrated embodiment, the end face on the step side 1 1 6 of the piston 1 12. The seal 138 leads to a sealing of the second compression chamber 106 with respect to the first compression chamber 104 and the compression chambers 104,106 relative to a crankcase interior 1 60. For this purpose, the seal 138 has an outer side 138.1 and an inner side 138.2. The outer side 138.1 of the seal 138 is on the outer periphery, so the outside of the - simplified described - arranged annular seal 138, thus providing a circumferential, continuous contact with a, in particular a cylindrical cavity-forming cylinder inner wall 1 19, ago. The inside 138.2 of the seal 138 is on the inside, ie on the inner periphery of the - simplified described - arranged annular seal 138 and thus establishes a circumferential, continuous contact with a web wall inside 109. By means of the arrangement and design of the piston 1 12, the cylinder 1 18 and the inner cylinder web 1 10 it is thus possible to effect a seal of both compression chambers 104, 106 with a comparatively small number of seals, in particular only a single seal 138.

In Fig. 2A is further the relative inclination of the piston 1 12 and of the piston 1 12 rigidly connected to the connecting rod 128 to the cylinder 1 18th visible, noticeable. This inclination is caused by the existing perpendicular to the stroke direction portion of the offset between the running through the point S1 axis of rotation of the drive shaft and passing through the point S2 rotation axis of rotation between connecting rod 128 and eccentrically arranged shaft portion 132. This perpendicular to the stroke direction existing proportion of the offset is dependent on the angular position of the drive shaft 102 and the eccentrically arranged shaft portion 132. At the top or bottom dead center of the piston 1 12, when the deflection H in the stroke direction is maximum, the perpendicular to the stroke direction existing proportion of the offset is equal to zero. On the middle of the path between the two dead centers of the piston 1 12, when the deflection H is equal to zero in the stroke direction, the proportion of the offset perpendicular to the stroke direction is correspondingly maximum.

By the relative inclination of the piston 1 12 and the connecting rod 128 to the cylinder 1 18 arise openings, in particular crescent-shaped gaps, between the piston 1 12 and the inner wall of the cylinder 1 18 and cylinder inner web 1 10. Such openings lead to an escape of compressed Air from the second compression chamber 106 in the first compression chamber 104 and / or in the environment U or in a crankcase interior 1 60. To avoid this, or to compensate for the wobbling movement of the piston 1 12, the seal 138 is designed accordingly. This includes a sufficient dimensioning and elastic behavior of the seal 138, so that even when caused by the wobbling openings between the piston 1 12 and cylinder 1 18, a seal of the compression spaces 104 and 106 is ensured.

Fig. 2B shows a further sectional view of a preferred embodiment of a compressor in a sectional plane parallel to both the drive and the piston axis A. From the sectional view can be seen how about a disposed within the piston 1 12 and the connecting rod 128 air supply port 120 air from the Environment U or the crankcase interior 1 60 can get into the first compression chamber 104. In this case, an air supply valve flap 142 arranged on the full side 1 14 of the piston 1 12 ensures that air can only flow into the first compression space 104 via the air supply connection 120, but not beyond. This is achieved by the air supply valve flap 142 closes against the increase in the first compression chamber 104 pressure at the caused by the deflection H reduction of the first compression chamber 104, and the associated compression of the air therein. Accordingly, when increasing the first compression space 104, the air supply valve flap 142 opens due to the negative pressure prevailing in the first compression space 104 relative to the environment, so that air from the environment or the crankcase interior 1 60 flows into the first compression space 104.

Furthermore, a check valve 130 is disposed within the piston 1 12 as a further connection between the first compression chamber 104 and the air supply port 1 20 and or the crankcase interior 1 60, which is held by a spring force F in the closed state. By the check valve 130 thus air in the first compression chamber 104, the pressure of which exceeds a certain, in particular for the compressor potentially harmful, maximum value, escape via the air supply port 120 into the environment. Alternatively, the check valve 130 may also be arranged such that the air directly, i. Without being guided via the air supply port 120, escapes into the crankcase interior 1 60 or the environment U.

Between the first compression chamber 104 and the second compression chamber 106, a connecting line 122 is furthermore arranged within the piston 1 12. This connection line 122 represents a gas-conducting connection of the two compression spaces 104 and 106 and, analogously to the air supply valve flap 142, has a connection valve flap 144 which ensures that air can only flow in one direction through the connection. Accordingly, the connection valve flap 144 closes when reducing the second compression chamber 106 against the increasing pressure and opens when enlarging, so that air from the first compression chamber 104 flow into the second compression chamber 106 can. The compressed air in the second compression chamber 106 can be made available via a compressed air outlet 124 to consumers of a pneumatic system 500, in particular via a compressed air supply system 200.

Furthermore, in the cylinder 1 18 a leading to the second compression chamber 106 charging port 126 is arranged, which has a Aufladeventilklappe 146. Via the charging port 126, the second compression chamber 106 air, which has been compressed, for example, at a previous time and stored in a pressure fluid reservoir 224 and stored, are supplied. In this way, the power of the compressor 100 can be increased in the short term, in particular to make compressed air faster available. The charging valve flap 146 ensures that air flows in via the charging port 126 exclusively into the second compression chamber 106 and can not escape via the charging port 126.

Furthermore, the piston 1 12 has no cylindrical shape, but one along a piston axis A variable cross-section. In this embodiment, the piston 1 12 at the level of the full page 1 14 has a cross section with a piston outside diameter KN. On the step side 1 1 6, however, the piston 1 12 has a piston main diameter KH, which is greater than the piston outside diameter KN. Because of these different diameters and the course of the piston diameter between the step side 1 1 6 and the full page 1 14 results in a variable, substantially non-cylindrical course of both an outer side 1 12.1 and an inner side 1 12.2 of the piston 1 12, the to leads that the piston 1 12 practically dome-shaped is trained. Such a design in particular a mobility of the piston 1 12 is achieved within the cylinder 1 18, this particular despite the tumbling motion of the piston 1 12th

The piston main diameter KH can not be greater than the diameter of the cylinder 1 18, but it is possible and even useful if the diameter of the outside 138.1 of the seal 138 is greater than the piston main diameter KH and also as the diameter of the cylinder 1 18. On this It is possible that the piston 1 12 together with the seal 138, despite the tumbling motion of the piston 1 12 and resulting openings and gaps between the piston 1 12 and cylinder 1 18 and piston 1 12 and web wall 1 1 1, a seal between the first compression chamber 104 and the second compression chamber 106 and between the second compression chamber 1 06 and the crankcase interior 1 60 manufactures. At the same time, the movement of the piston 1 12, despite the larger diameter of the outer side 138.1 of the seal 138, not substantially hindered or blocked, since the seal 138 is preferably formed of an elastic material.

3 shows a sectional view of a compressor 100 according to the concept of the invention in the installed state. A drive shaft 102 is disposed such that one end of the drive shaft 102 is within the compressor housing 154, in which the corresponding end portion of the drive shaft 102, supported by a drive shaft bearing 150, is guided through an opening in the compressor housing 154.

On the guided into the compressor housing 154 end portion of the drive shaft 102, an eccentric 132 is attached. This eccentric 132 has a cylindrical connecting rod receiving portion 156, on which the connecting rod bearing 152 is attached. The axis of rotation of the cylindrical connecting rod receiving portion 156 is arranged parallel to the axis of rotation of the drive shaft 102, but with a certain, required to fulfill the Eccentric effect or reaching a deflection H offset. The eccentric 132 furthermore has a counterweight section 158 arranged opposite the connecting rod receiving section 156 in the radial direction. The counterweight section 158 serves, in particular, for the compensation or the at least partial extinction of inertial forces which act on the eccentric 132 via the connecting rod 128 connected to the eccentric 132 due to the rotational movement.

The connecting rod 128 is rotatably connected to the connecting rod receiving portion 156 via a connecting rod bearing 152. By caused by the rotational movement of the eccentric 132 deflection of parallel to the cylinder axis of the cylinder 1 18 aligned movement portion of the deflection causes an oscillating stroke movement of the piston 1 12 within the cylinder 1 18th

The piston 1 12 carries on its step side 1 1 6 a seal 138 for sealing the second compression chamber 106 with respect to the first compression chamber 104 and against the environment.

The piston 1 12 is shown in this illustration, practically at the top dead center, that is, with its approximate minimum volume having first compression chamber 104 and its approximate maximum volume having second compression chamber 106th

The shape of the piston 1 12 is formed in this case practically dome-shaped, so that the piston is designed to match a dome-shaped portion 1 64 of the cylinder 1 18. This means in particular that both the inner cross section 1 12.2 and the outer cross section 1 12.1 of the piston in the axial direction of the piston 1 12 are changeable, in particular such that both cross sections 1 12.1, 1 12.2 in the course of the step side 1 1 6 for Full side 1 14 decrease along a piston axis A, in particular the diameter is smaller. Such a design of the piston 1 12 leads to the advantage that the tumbling movement of the piston 1 12 can be compensated particularly well, in particular despite the tumbling motion, a sealing of both compaction ment spaces 104, 106 can be achieved with each other and with respect to the crankcase interior 160 and still there is no risk of tilting of the piston 1 12. This is achieved by the fact that the piston at the axial height of the seal 138 has its greatest radial extent, ie its largest outer cross-section 1 12.1. Furthermore, this region of the largest outer cross section has a small axial height, ie, the section with the largest outer diameter or with contact with the inner wall of the cylinder 1 18 is kept relatively flat. This minimizes friction and, in particular, the risk of piston and cylinder tilting despite the tumbling motion. Also, an elastic deformability of the seal 1 38 causes occurring during the tumbling motion openings, in particular crescent-shaped gaps, between the piston 1 12 and the cylinder 1 18, can be sealed by the seal 138.

In addition to a dome-shaped design of the piston, this advantageous reduction of the risk of tilting can be achieved with other, tapering to the full side of the piston designs, for example, by a conical or similar outer shape.

Similarly, the piston 1 12 is also on its inside, d. H. the inner cross section 1 12.2 only via the seal 138 with the web wall 1 1 1 of the cylinder inner web 1 10 in contact. By this smallest radial expression of the inner cross section 1 12.2 only in the axial region of the seal 138 is - similar to the outer cross section 1 12.1 - a low degree of friction and a smaller risk of tilting, especially during a tumbling motion of the piston guaranteed.

Also, the present, hollow design of the piston leads to an advantageously space-saving design, especially since the interior of the dome provides movement space for the moving relative to the cylinder web wall 1 1 1, and in this way the first compression chamber 104 and the second compression chamber 106 a smaller Distance along the column have A axis. Furthermore, the air supply port 120 arranged in this embodiment within the compressor housing 154 and leading to the first compression chamber 104 is shown. The compressed air outlet 124, which is likewise arranged inside the compressor housing 154, connects the second compression chamber 106 with the compressed air supply system 200. The compressed air compressed in the second compression chamber 106 is thus provided via the compressed air outlet 124.

FIG. 4A shows a detailed view of a piston 12 of a still further embodiment in a sectional plane perpendicular to the drive axis. The features shown therein essentially correspond to the features already shown symbolically in FIG. 2A - accordingly, identical or similar features or features with identical or similar functions are provided with the same reference numerals.

The shape of the piston 1 12 is also present in this case practically dome-shaped, so that the piston is designed to match a dome-shaped portion 1 64 of the cylinder 1 18. The piston 1 12 has an outer side 1 12.1 and an inner side 1 12.2. In particular, the piston 1 12 - analogous to the embodiment shown in Fig. 3 - suitable by its dome-shaped expression, despite its tumble kinematics in a predominantly cylindrical trained or - as here present - dome-shaped interior of a cylinder 1 18 to move.

The seal 138 with an outside 138.1 and an inside 138.2 is also clearly recognizable. The outer side 138.1 is in this case over the outer circumference of the seal 138 peripherally in contact with a cylinder inner wall 1 19, so that a pressure-tight seal against a first compression space 104 is effected. The inside 138.2 of the seal 138 is circumferentially in contact with a web wall inside 109 over the inner periphery of the seal 138, so that a pressure-tight seal against a crankcase interior 1 60 is effected. Furthermore, in the present case, the piston 1 12, in particular the dome portion 1 64 of the Piston 1 12, by means of a piston screw 1 66 attached to a connecting rod 128. Of the connecting rod 128, only the piston side 128.1 is visible in the present view.

4B shows a detailed view of a piston 12 of the still further embodiment in a sectional plane parallel to both the drive and the piston axis. In contrast to the view in FIG. 4A, a check valve 130, an air supply connection 120, a connection line 122, an air supply valve flap 142, a connection valve flap 144, a charge valve flap 146 and a compressed air outlet 124 and a charge connection 126 are particularly visible. These features essentially correspond to the features already shown symbolically in FIG. 2B - accordingly, identical or similar features or features with identical or similar functions are provided with the same reference numerals.

A difference from the embodiment shown in FIG. 2B is that the air supply valve flap 142 and the check valve 130 are not connected together as shown in FIG. 2B to an air supply port 120 guided by a connecting rod 128, but arranged separately in the piston 1 12 and gas-conducting connected to a crankcase interior 1 60 - or connectable to the check valve 130 in response to the spring force - are.

FIGS. 5A and 5B show an embodiment of a seal 138a that substantially corresponds to a previously described seal 138. The seal 138a comprises a sealing body 139a, which has a first annular lip 139.1a and a second annular lip 139.2a. The first annular lip 139.1a is arranged in a radial direction RR on the outside of the sealing body 139a such that it extends in an axial direction RA in the direction of a second compression chamber 106. The first and / or second annular lips 39.1 a, 139.2a in particular has a free end, which is arranged in the second compression chamber 106. The second annular lip 139.2a is disposed in a radial direction RR inside the sealing body 139a. It also extends in an axial direction RA in the direction of the second compression chamber 106. The sealing body 139a is attached to a step side 1 16 of a piston 1 12 - this is shown in Fig. 5B.

The first annular lip 139.1 a is rotationally symmetrical about the piston axis A and has a profile which, starting from a main body 139.4a, initially extends radially outward in the radial direction RR and then changes its direction by approximately 90 °, so that it extends in the axial direction RA in the direction of the second compression chamber 106, in such a way that an outer side 138.1 a of the seal 138a substantially parallel to the cylinder inner wall 1 19, namely to a wall outer side 1 19.1 of the cylinder inner wall 1 19. This profile creates a first expansion space 139.5a between the main body 139.4a and the first annular lip 139.1a.

The second annular lip 139.2a is likewise rotationally symmetrical about the piston axis A and has a profile which, starting from the main body 139.4a, initially extends inward in the radial direction RR and then changes its direction by approximately 90 ° so that it extends in the axial direction RA in the direction of the second compression chamber 106 in such a way that an inner side 138.2a of the seal 138a to the cylinder inner wall 1 19, namely to a wall inner side 1 19.2 of the cylinder inner wall 1 19, is arranged in parallel. This profile creates a second expansion space 139.6a between the main body 139.4a and the second annular lip 139.2a.

By the first and the second expansion space 139.5a, 139.6a causes the first and the second annular lip 139.1 a, 139.2a are pressed by a prevailing in the second compression chamber 106 second pressure P2 to the cylinder inner wall 1 19 and thus a seal of the second Compaction space 106 both compared to the first Compression space 104, as well as the crankcase interior 1 60 cause. In this case, the first expansion space 139.5a causes the first annular lip 139.1a to be pressed against the wall outer side 19.1, which leads to a first seal AD1. The first seal AD1 is, as long as the second pressure P2 is greater than or equal to a prevailing in the first compression chamber 106 first pressure P1. The second expansion space 139.6a causes the second annular lip 139.2a is pressed against the inner wall side 19.1.1, resulting in a second seal AD2. The second seal AD2 is, as long as the second pressure P2 is greater than a prevailing in the crankcase interior 1 60 external pressure PA.

FIGS. 5C and 5D show another embodiment of a seal 138b. The essential difference of the seal 138b to the seal 138a shown in FIGS. 5A and 5B is that a sealing body 139b of the seal 138b has, in addition to a first annular lip 139.1b and a second annular lip 139.2b, an additional third annular lip 139.3b a radial direction RR is disposed on the outside of the sealing body 139 b and is directed in an axial direction RA to the first compression space 104. The third annular lip 39.3b in particular has a free end which is arranged in the first compression chamber 104.

The third annular lip 139.3b is rotationally symmetrical about the piston axis A and has a profile which, starting from a main body 139.4b, initially extends radially outward in the radial direction RR and then changes its direction by approximately 90 °, so that it extends in the axial direction RA in the direction of the first compression chamber 104, in such a way that an outer side 138.3b of the seal 138b is arranged substantially parallel to the cylinder inner wall 1 19, namely to a wall outer side 1 19.1 of the cylinder inner wall 1 19. This profile creates a third expansion space 139.7b between the main body 139.4b and the third annular lip 139.3b. By the third expansion chamber 139.7b causes the third annular lip 139.3b is pressed by a prevailing in the first compression chamber 104 first pressure P1 to the cylinder inner wall 1 19 and thus causes a seal of the first compression chamber 104 relative to the second compression chamber 106.

In this case, the third expansion space 139.7b causes the third annular lip 139.3b to be pressed against the wall outer side 19.1 by the first pressure P1, which leads to a third seal AD3. Such a development with a third annular lip 139.3B has the advantage that the first seal AD1 and the third seal AD3 are independent of a pressure difference between the first pressure P1 and the second pressure P2. Thus, a reliable seal between the first compression chamber 104 and the second compression chamber 106 can take place. In particular, in contrast to the embodiment shown in FIGS. 5A, 5B, a sealing between the first compression chamber 104 and the second compression chamber 106 can also take place if a first pressure P1 in the first compression chamber 104 is equal to or greater than a second pressure P2 This is particularly the case in a one-stage operating mode of a compressor 100, ie an operating mode in which air in both compression spaces 104, 106 is compressed to the same pressure.

List of Reference Numerals (part of the description):

1 total compressed air supply

2 compressed air connection, first compressed air connection

2 'Second compressed air connection

3 exhaust connection

10 compressed air supply

30 Pneumatic main

31 First isolation valve

32 check valve

33 bypass line

34 throttle

35 vent line

36 Further isolation valve

37 pneumatic line

38 Still another isolation valve

39 Another check valve

40 Further pneumatic line

41 second isolation valve

51 suction line

52 filters

100 compressors

102 drive, drive shaft

104 First compression chamber, first compression chamber

106 Second compression chamber, second compression chamber

109 web wall inside

1 10 cylinder inner web

1 1 1 web wall

1 12 pistons, reciprocally pressurizable pistons

1 12.1 External cross section, outside of the piston

1 12.2 Inner cross-section, inside of the piston

1 13 First end of the piston 1 14 full page

1 15 Second end of the piston

1 1 6 step side

1 18 cylinder

1 19 cylinder inner wall

1 19.1 Wall outside of the cylinder inner wall

1 19.2 Wall inside of the cylinder inner wall

120 air supply connection

122 connection line

124 compressed air outlet

126 Charging port

128 connecting rods

128.1 Piston side of the connecting rod

128.2 Drive side of the connecting rod

130 check valve

131 Rotating part of the drive

132 Eccentrically arranged shaft section, eccentric

138 seal

138.1 Outside of the seal

138.2 Inside of the seal

139, 139a, 139b sealing body

139.1 a, 139.1 b First ring lip

139.2a, 139.2b Second ring lip

139.3b Third ring lip

139.4a, 139.4b Main body of the seal body

139.5a, 139.5b First expansion room

139.6a, 139.6b Second expansion space

139.7b Third expansion area

142 Air intake valve flap

144 connection valve flap

146 Charging valve flap 150 drive shaft bearings

152 connecting rod bearings

154 compressor housing

156 connecting rod receiving section

158 counterweight section

160 crankcase interior

62 Rotary connection

164 dome section of the cylinder

166 piston screw

200 compressed air supply system

210 air spring

21 1 Air bellows, bellows

212 air spring valve

220 Gallery, gallery management

221 spring branch line

222 air dryer

224 fluid reservoir, accumulator

230 voltage-pressure sensor

300 pneumatic system

400 vehicle

410 supports

500 pneumatic system

A piston axis

AD1 First seal

AD2 Second seal

AD3 third seal

B Ventilation direction

D Percentage of offset existing to the stroke direction

E Venting direction

E 'Further ventilation direction

F Spring force of the check valve H deflection, deflection of the piston in the stroke direction

KH piston main diameter

KN piston diameter

M engine

P1 First pressure, pressure in the first compression chamber

P2 Second pressure, pressure in the second compression chamber

PA external pressure, pressure in the crankcase interior

RA Axial direction

RR Radial direction

51 axis of rotation of the drive, point S1

52 axis of rotation of the rotatable connection between

Connecting rod and eccentrically arranged shaft section, point S2

U environment

Claims

claims

1 . Compressor (100), in particular compressor, for a compressed air supply (10) of a compressed air supply system (200), for operating a pneumatic system (500), comprising: a first compression chamber (104), a second compression chamber (106), an air supply connection (120) and a compressed air outlet (124), a piston (1 12) with a first pressurizable end face (1 13) which is directed to the first compression chamber (104) and one, the first end face (1 13) opposite, second pressurizable end face (1 15), which is directed to the second compression chamber (106), wherein the first compression space (104) from the first end face (1 13) is limited and the second compression chamber (106) from the second end face (1 15) of the piston (1 12) is limited , wherein the first end face (1 13) is a full side (1 14) and the second end face (1 15) is a step side (1 1 6), and the piston (1 12) via a connecting rod (128) to a drive ( 102) nden is, wherein the first compression chamber (104) and the second compression chamber (106) via a connecting line (122) are interconnected, characterized in that the connecting rod (128) rigid, in particular rigid and articulated, on a piston side (128.1) with the piston (1 12) is connected and on a drive side (128.2) with a rotating part (131) of the drive (102) is rotatably connected, and the piston (1 12) on the step side (1 1 6) carries at least one seal (138) which seals the first compression space (104) and / or the second compression space (106).

2. Compressor (100) according to claim 1, characterized in that the piston (1 12) from the first compression chamber in the direction of the air supply port (120) automatically against a spring force (F) opening check valve (130).

3. The compressor (100) according to claim 1, characterized in that the connecting rod (128) with the rotating part (131) of the drive (102) in the form of an eccentrically arranged shaft portion (132) is rotatably connected.

4. The compressor (100) according to any one of the preceding claims, characterized in that the connecting rod (128) is integrally formed with the piston (1 12) and with respect to the piston (1 12) articulated.

5. Compressor (100) according to one of the preceding claims, characterized in that the first compression space (104) is cylindrical or cylindrical with dome-shaped portion (1 64) and / or the second compression space (106) is annularly cylindrical.

6. The compressor (100) according to any one of the preceding claims, characterized in that the seal (138) for sealing the second compression chamber (104) against a crankcase interior (1 60) and / or the environment (U) and / or for sealing the first compression space (104) is formed against the second compression space (106).

7. compressor (100) according to any one of the preceding claims, characterized in that the at least one seal (138) on the step side (1 1 6) of the piston (1 12) both on an outer side (138.1) and on an inner side ( 138.2) acting in the radial direction pressure-tight seal causes, in particular as a single seal (138) is formed.

8. The compressor (100) according to claim 7, characterized in that the outer side (138.1) of the seal (138) circumferentially in contact with a cylinder inner wall (1 19) and the inner side (138.2) of the seal (138) circumferentially in contact with a web wall inside (109) stands.

9. A compressor (100) according to claim 7, characterized in that the seal (138, 138 a, 138 b) an annular sealing body (139,

139a, 139b) with a first annular lip (139.1a, 139.1b) radially on the outside of the sealing body (139, 139a, 139b) and a second annular lip (139.2a, 139.2b) radially inward on the sealing body (139, 139a, 139b).

10. A compressor (100) according to claim 7, characterized in that the seal (138a, 138b) has an annular sealing body (139a, 139b) comprising: a first annular lip (139.1 a, 139.1 b), in the radial direction (RR) on the outside of the sealing body (139a, 139b), in the axial direction (RA) directed towards the second compression chamber (106), and / or a second annular lip (139.2a, 139.2b), in the radial direction (RR) inside of the sealing body (139a, 139b), in the axial direction (RA) to the second compression space (106) directed, is arranged.

1 1. Compressor (100) according to claim 10, characterized in that the annular sealing body (139b) has a third annular lip (139.3b), in the radial direction (RR) outside of the sealing body (139b), in the axial direction (RA) to the first compression space (104) directed, is arranged.

12. Compressor (100) according to any one of the preceding claims, characterized in that the piston (1 12) has a variable in the axial direction, non-cylindrical outer cross-section (1 12.1).

13. The compressor (100) according to any one of the preceding claims, characterized in that the second compression chamber (106) further comprises a charging port (126) for additionally supplying compressed air, in particular from a pressure medium reservoir (224).

14. The compressor (100) according to any one of the preceding claims, characterized in that the air supply port (120) within the connecting rod (128) and / or the piston (1 12) is arranged.

15. The compressor (100) according to any one of the preceding claims, characterized in that the rotatable connection (1 62) between the connecting rod (128) and an eccentrically arranged shaft portion (132) of the drive (102) by means of a connecting rod bearing (152) - in particular a plain bearing, ball bearing or needle bearing - is formed.

16. A compressed air supply system (200) for operating a pneumatic system (300), comprising: an air supply and a compressor (100) connected thereto via an air supply connection (120) according to one of the preceding claims, one to the compressor pneumatically via a compressed air outlet (124). 100) connected to a compressed air connection (2) of a gallery (220), an air dryer (222) having a pneumatic main line (30), a via a charge port (126) pneumatically to the compressor (100) connected pressure fluid reservoir (224).

17. A method for operating a compressed air supply system (200) according to claim 1 6 comprising the steps:

Compressing air from a crankcase interior (1 60) and / or the environment (U) in a first compression chamber (104) of the compressor (100) to a low pressure level, further compressing the compressed air compressed in the first compression chamber (104) to a low pressure level in a second compression chamber (106) of the compressor (100) to a high pressure level,

Supplying compressed air compressed in the second compression chamber (106) to a high pressure level from the compressed air outlet (124) via a main pneumatic line (30) to a compressed air connection (2) of a gallery (220), in particular via an air dryer (222).

18. Vehicle (400) with a compressed air supply system (200) according to claim 1 6.