WO2017016644A1

WO2017016644A1 - Compressor

Info

Publication number: WO2017016644A1
Application number: PCT/EP2016/001199
Authority: WO
Inventors: Kurt Koch
Original assignee: Kurt Koch
Priority date: 2015-07-24
Filing date: 2016-07-12
Publication date: 2017-02-02
Also published as: DE202015005274U1

Abstract

The invention relates to a compressor having at least one cylinder (24), which has an internal wall (23), and a piston (26) that is rotatably mounted in the cylinder (24), eccentrically with respect to the longitudinal axis (25) of the latter, and that has a circular cross section (27), wherein the outer diameter (30) of the piston (26) is smaller than the inner cross section of the cylinder (24) so as to form at least one compression space (31), and the piston (26) is in sealing contact with the internal wall (23) of the cylinder (24) and has a device (32) that can move in the radial direction of the piston (26), is also in sealing contact with the internal wall (23) of the cylinder (24) and rotates with the piston (26).

Description

Kompressionsvorrichtunq

The invention relates to a compression device.

A conventional turbocharger, such as an exhaust gas turbocharger of a gasoline engine, has a turbine and a compressor. These components can be constructed very similar and mounted on a common shaft. The exhaust gas stream sets the turbine wheel in rotation. Its torque is transmitted via the common shaft to the compressor wheel in the intake system. As long as sufficient exhaust flows to the turbine wheel, the speed is sufficient to cause an overpressure on the intake side. However, this condition is reached only at higher engine speeds from about 1500 to 2000 min ^-1 , so that turbo engines in the lower speed range only work as naturally aspirated and delayed when retrieving a higher power at higher speeds with a conventional "turbo lag".

The invention has for its object to provide a compression device which is operable efficiently.

This object is achieved by a compression device with the features of claim 1. Advantageous developments are the subject of the dependent claims. The compression device according to the invention has at least one cylinder having an inner wall and a piston rotatably mounted in the cylinder eccentric to the longitudinal axis of circular cross-section, wherein the outer diameter of the piston for the formation of at least one compression space is smaller than the inner cross section of the cylinder and the piston in sealing contact with the inner wall of the cylinder is and has a movable in the radial direction of the piston means, which is also in sealing contact with the inner wall of the cylinder and rotates with the piston. This device may have a lower mass than, for example, a traditional turbocharger due to its higher efficiency. Already for this reason, the compression device according to the invention with the same power with less energy consumption is operable. The aforementioned construction principle of the compression device can be manufactured at comparable performance at a lower production price compared to a conventional turbocharger. This construction principle requires less weight per unit of power. Due to the simplified construction principle and the lower dead weight, the compression device can be operated at the same power with significantly less energy. It can be operated much easier with simple means without special technical effort. The compression device according to the invention can, especially if several units are connected together to form a compressor group, and even in the very low speed range to develop a comparatively high performance, without such operation harms the technical parts or the mechanical components. In addition, the noise will be reduced compared to the conventional turbocharger, which also reduces the effort for the damping. The dimensions of the compression device, its mass and weight are lower compared to the conventional turbocharger. It follows that at the same power the compression device has a lower weight than a corresponding conventional turbocharger. In this respect, the manufacturing and operating costs are reduced in the compression device according to the invention compared to a built-up in a known manner turbocharger corresponding power. This construction principle of the compression device makes it possible to use this instead of a turbocharger in a gasoline engine. This will increase performance in practice already reached from the first revolution of the engine. The compressed air generated by the compression device or the air mixture or fuel / air mixture can be passed in a simple process in a buffer memory and also flexibly retrieved and initiated as needed or calculation in the cylinder or the engine. Engine management can easily make it possible to adjust the volume of the absorbed and finally compressed or compressed air according to the demand per working cycle. Thus, the compression device can thus be designed and operate as a compressor or compressor.

Advantageously, the movable in the radial direction of the piston means comprises two diametrically opposed wing parts, each biased radially outwardly biased against the inner wall of the cylinder. It is advantageous that such a compression device per revolution allows two compression or compression strokes. This results in a high efficiency for the compression device according to the invention. It runs like a simple AC motor always round and develops its two compression strokes per revolution during the orbit. Complicated valve controls can be omitted. The two diametrically opposite wing parts allow so far two compression strokes per revolution.

According to one embodiment of the invention, the wing parts are guided in the piston guided by spring force and / or provided in the piston connecting channels using the compressed air or a compressed fuel / air mixture radially outward to the inner wall of the cylinder. In this respect, a sliding contact of the wing parts along the inner wall of the cylinder by simple means can be brought. The compressed air or the air mixture can also contribute to the fact that the wing parts are constantly in contact with the inner wall of the cylinder.

According to a particularly advantageous development, the cylinder has inlet and outlet valves for the fluid or fluid mixture involved in the compression process. In this respect, a rotary engine before each power stroke could compressed air or a compressed fuel / air mixture obtained in the combustion chamber of its cylinder. The rotary engine would therefore have to compress no more air and no air mixture more. In contrast, prior to a power stroke, a conventional gasoline engine must compress the trapped air, with the volume of air possibly being increased by a charging device such as a turbocharger. In the Otto engine, therefore, the amount of air available for combustion without additional charging device corresponds approximately to the cylinder contents. The compression device can be designed in any desired volume. In a gasoline engine with a turbocharger, the effect of the supercharger usually starts at a certain speed. In the compression device according to the invention, however, the full power with the supplied compressed air or the compressed fuel / air mixture sets in already from the first revolution. According to another embodiment of the invention, a free-running sealing plate is arranged on the head parts of the cylinder, which has on its wegführenden from the piston outer side grooves for a lubricant, wherein the grooves are preferably arranged at an acute angle obliquely to the radial direction of the sealing plate. Such sealing plates meet, greatly simplified, approximately the function of the piston rings in a reciprocating engine. Such an arrangement of the grooves makes it possible for the rotating sealing plates simultaneously to function as a circulating pump for the lubricant, for example an oil lubrication, in the sense of a double function. As a result, the expenditure on equipment of the compression device according to the invention can be further reduced. Good lubrication allows lossless running as possible of the compression device according to the invention.

According to a preferred refinement, cylinder head covering plates with lubricant channels are arranged on the head sides of the cylinder such that the lubricant channels open into the region of the grooves provided on the respective sealing plate. In this way, the lubricant can be easily passed to the sealing plates and thus to those locations and areas where lubrication should be provided. Embodiments of the subject invention are described below with reference to the drawings, all described and / or illustrated features alone or in any combination form the subject matter of the present invention, regardless of their combination in the claims or their dependency. Show it:

1 shows a schematic section through a compression device in a first working position;

Fig. 2 is a schematic section through the compression device according to

Fig. 1 in a second working position;

Fig. 3 is a schematic section through the compression device according to

Fig. 1 in a third working position;

Fig. 4 is a schematic section through the compression device according to

Fig. 1 in a fourth working position;

Fig. 5 is a schematic section through the compression device according to

Fig. 1 in a fifth working position;

6 shows a schematic section through the compression device according to FIG. 1 in a sixth working position;

7 shows a schematic section through the compression device according to another embodiment in an enlarged view;

8 shows a schematic, partial longitudinal section through the compression device;

Fig. 9 is a schematic front view of a seal plate of the compression device; and

10 is a schematic section through a compression device according to another embodiment.

In Fig. 1 is a schematic, partial cross section through a compression device 2 according to a first embodiment is shown. The compression device 2 is, for example, a compressor or a compressor.

The compression device 2 has at least one cylinder 24, which has an inner wall 23. The cylinder 24 has in the one shown in FIG Embodiment a circular cross-section. But it is also possible that the cylinder has a different, in particular an elliptical cross-section.

Further, the compression device 2 has a piston 26 which is rotatably mounted in the cylinder 24 eccentrically to the longitudinal axis 25 thereof. The longitudinal axis 25 of the cylinder 24 is shown in Figs. 1 and 8.

The piston 26 has a circular, namely circular cross section 27. The outer diameter 30 of the piston 26 is for the formation of at least one compression space 31 smaller than the inner cross section of the cylinder 24, which is formed as shown in FIG. 1 as a circular surface with the inner diameter 28.

The piston 26 is shown in FIGS. 1 to 7 in sealing contact with the inner wall 23 of the cylinder 24. The piston 26 has a movable in the radial direction of the piston 26 means 32, which also in sealing contact with the inner wall 23rd of the cylinder 24 and rotates with the piston 26. The movable in the radial direction of the piston 26 means 32 has two diametrically opposite wing portions 33, 34. The wing portions 33, 34 are respectively radially outwardly biased in the inner wall 23 of the cylinder 24 at. This is shown in an enlarged view in Fig. 7. The wing portions 33, 34 are guided in the piston 26 guided by spring force and / or provided in the piston 26 connecting channels 37, 38 by means of the compressed compressed gas radially outward to the inner wall 23 of the cylinder 24 out. The connecting channels 37, 38 are omitted in FIGS. 1 to 6 for the sake of simplicity and shown in more detail only in Fig. 7. The springs 20 shown in Fig. 7 are therefore compression springs.

Further, the cylinder 24 for the fluid or fluid mixture involved in the compression process inlet and outlet valves 51, 54, 77, 82; 22. Further, the aforementioned compression device 2 may be arranged and configured such that via the outlet valve 22 of the cylinder 24 compressed air or a compressed fuel / air mixture in a combustion chamber not shown in detail of an engine (not shown) can be introduced. The compressed air or the compressed fuel / air mixture thus passes from the compression device 2 via the exhaust valve 22, which may also serve as an intake valve for an engine, into the combustion chamber of a cylinder of the engine.

The exhaust valve 22 of the cylinder 24 involved in the compression process can thus form the inlet valve of a motor not shown in detail and be formed as a valve 36 for passing the compressed air or the compressed fuel / air mixture into the combustion chamber of the engine. The latter valve 36 may be referred to simply as a transfer valve.

The piston 26 of the compression device 2 is drivingly connected, for example, with a not shown piston of a cylinder involved in the combustion process (not shown in detail) and driven by the latter. As an alternative for the piston, an electric motor could also be provided in a vehicle engine. As shown in Fig. 1, the piston 26 rotates in the counterclockwise direction as shown by the arrow B. In Fig. 8 is a schematic representation of a partial longitudinal section through the cylinder 24 is shown.

In the head sides 40, 41 of the cylinder 24, a free-running sealing plate 42 is arranged in each case. Such a sealing plate 42 is shown in a schematic front view in Fig. 9. The seal plate 42 has on its side facing away from the piston 26 outside 43 grooves 44 for a lubricant. The grooves 44 are arranged at an acute angle 45 obliquely to the radial direction of the seal plate 42. According to FIG. 8, cylinder head cover plates 46, 47 are arranged on the head sides 40, 41 of the cylinder 24. The cylinder head cover plates 46, 47 have lubricant passages 50 which open into the region of the grooves 44 provided on the respective seal plate 42. The grooves of the Sealing plate 42 are omitted in the representation shown in Fig. 8 for the sake of clarity.

The operation of the compression device 2 will be explained in more detail with reference to FIGS. 1 to 6.

FIG. 1 shows that working position in which the compressed air 55 has almost completely left the cylinder 24 via the outlet valve 22 or the bypass valve 36. The exhaust valve 22 will soon be closed. According to the embodiment shown in FIG. 7, in addition to the inlet valve 54, a further inlet valve 51 is also provided, via which air can be introduced into the compression space 31. The further inlet valve 51 can serve to introduce fresh air into a second cylinder chamber 60 of the compression space 31 in order to avoid a vacuum therein or to produce a pressure compensation. However, the further inlet valve 51 can also be dispensed with (see FIGS. 1 to 6).

Pistons 26 and vane members 33, 34 in the cylinder 24 of the compression device 2 are arranged such that the exhaust valve 22 / bypass valve 36 is closed by the wing member 34 shortly and the inlet valve 54 of the compression device 2 is already partially closed by the wing member 33 of the device 32 becomes. In this respect, in the position shown in FIG. 1, the compression space 31 is almost completely filled with fresh air. The beginning of the compression process is imminent. A further movement of the piston 26 in the direction of arrow B leads to the second operating position shown in FIG. 2. Here, the outlet valve 22 / transfer valve 36 is closed.

The introduced into the compression chamber 31 air is compressed by further rotation of the piston 26 by means of the wing portion 33. Via the inlet valve 54, the pressure compensation in the second cylinder chamber 60 of the cylinder 24 can take place. As a result, fresh air flows in the direction of the arrow E into the second cylinder chamber 60. The wing portion 34 of the piston 26 is located almost completely in the piston. It is clear that the wing parts 33, 34 are displaceably guided in the direction of the double arrows F in the piston (see FIG. 2).

A third working position of the piston 26 is shown in Fig. 3.

Again, the piston 26 has moved further including its means 32 in the direction of arrow B. In the compression device 2, the air in the compression space 31 is further compressed. Fresh air can continue to flow via the inlet valve 54 in the direction of arrow E in the second cylinder chamber 60 of the cylinder 24. The wing portion 34 is located entirely within the piston 26 and lies directly opposite a pressure device 61 for sealing between the cylinder 24 and the piston 26. The pressure device 61 may be a hydraulic, pneumatic or mechanical pressure device. Upon further movement of the piston in the direction of the arrow B, this finally reaches the fourth working position according to FIG. 4.

In the compression chamber 31, the already highly compressed air is further compressed. Fresh air also passes into the second cylinder chamber 60 via the inlet valve 54 (see arrow E).

In the fifth operating position according to FIG. 5, the compressed air in the compression space 31 is further compressed in the cylinder 24 of the compression device 2. The outlet valve 22 / bypass valve 36 will soon open, so that the highly compressed air 55 in the direction of the arrow A can flow out of the compression space 31 of the cylinder 24, as indicated in Fig. 6.

As soon as the highly compressed air 55 has completely left the cylinder 24, the outlet valve 22 / transfer valve 36 is closed. The working positions explained with reference to FIGS. 1 to 5 are repeated twice per complete revolution of the piston. Fresh air flows via the inlet valve 54 into the compression chamber 31 (see arrow E). In Fig. 7, the cylinder 24 of the compression device 2 according to another embodiment is shown in an enlarged view partially in section.

Between the compression space 31 and the second cylinder chamber 60 and the free base space 63 of each wing portion 33, 34 of the connecting channel 37, 38 is incorporated, so that each free base space 63 communicates with the compression chamber 31 and the second cylinder chamber 60. As a result, the compressed air can at least temporarily reach the free base space; it is therefore guided under the respective wing part 33, 34, whereby the respective wing part in the radial direction applied to the outside is sealingly pressed against the inner wall 23 of the cylinder 24 at least when the air flowing into the base space 63 or the mixture is compressed. The wing portions 33, 34 are guided by a slide pin 64 so that the slide pin serves as a seat for the inner end of each wing portion and the inner end of each wing portion circumferentially surrounds the respective end of the slide pin. The reference numeral 65 denotes the axis of rotation of the piston 26. The axis of rotation 65 corresponds to the longitudinal axis of the piston.

According to FIG. 7, the pressure device 61 comprises a pressure line 70, which is connected via an intermediate piece 71 to a pressure unit 72. The pressure unit 72 acts on a sealing structure 73, which seals the cylinder 24 with respect to the piston 26. The pressure line 70 may be a hydraulic or compressed air line. The pressure structure 73 may, as shown in FIGS. 1 to 6, in one piece or, as indicated in Fig. 7, be formed of several parts.

Fig. 8 shows a partial longitudinal section through the cylinder 24 of the compression device 2. At the head sides 40, 41 is located in the inner cross section of the cylinder 24 at each end of the seal plate 42. Each seal plate has a central inner bore 74. Each seal plate is free and moves , moved only by wing parts 33, 34, on a circular path. Since each seal plate 42 oscillates about a drive shaft 75, the inner bore 74 is larger than the outer diameter of the drive shaft 75, as shown in FIG. 8 can be seen. In Fig. 8 also the center line or longitudinal axis 25 of the cylinder 24 and the Longitudinal axis 65 of the piston 26 shown, the latter corresponds to the axis of rotation of the piston 26.

By arranging the aforementioned grooves 44 on the outer side 43 of each seal plate 42, each of the plates operates as a separate lubricant pump and thereby keeps the lubricant, such as a lubricating oil, in circulation. The direction of rotation of the cover plate 42, as shown in Fig. 9, is indicated by the arrow G. In Fig. 8, the longitudinal axis 65 of the piston 24 corresponds to its axis of rotation.

FIG. 10 shows a schematic, partial cross section through a further embodiment of the invention.

In the embodiment shown here, the cylinder 24 of the compression device 2 is larger than the cylinder shown in FIGS. 1 to 6. In this example, therefore, a larger amount of air for the compression process can be provided.

Another difference of the embodiment shown in Fig. 10 is that the compression device 2 operates here in the suction mode with respect to a fuel / air mixture. The cylinder 24 of the compression device 2 has an intake valve 77 connected to a carburetor 80. In this embodiment, the volume of the aspirated fuel / air mixture can be optimally selected depending on the location or seat of the carburetor 80 and the intake valve 77 to the cylinder 24.

A further special feature of the embodiment shown in FIG. 10 is that a further inlet valve 82 is provided in the compression space 31 for its filling. Compressed air can be passed via a line 81 to the further inlet valve 82 of the cylinder 24 of the compression device 2 and flow into the compression space 31.

The further inlet valve 82 serves, in particular, for directing precompressed air into the compression space 31 of the cylinder 24 of the compression device 2. If necessary, in the embodiment shown in Fig. 10, the inlet valve 54 shown in Figs. 1 to 6 may be additionally provided.

In the piston 26 thus work in the longitudinal direction, centrically aligned and radially movable, two-part wing parts 33, 34 in the space provided for them free base spaces 63. The wing parts may also be called "paddle". They are always outwardly by spring and / or gas pressure, i. are biased towards the inner wall of the cylinder and so are constantly in sealing contact with the inner wall of the cylinder in question. The rotatable piston 26 is fixedly pressed against the pressure device 61 in the wall of the respective cylinder 24. The outlet valve 22 / transfer valve 36 may be, for example, a rotating perforated disc with valve function.

The process described with reference to FIGS. 1 to 6 is repeated twice within one revolution of the piston, so that the compression device according to the invention operates extremely effectively. The compression device according to the invention can be used particularly advantageously like a compressor up to medium pressures. It can be used as a replacement for a turbocharger in gasoline engines. The efficiency and technical design of the device with rotary piston are clearly superior to the traditional turbocharger, since the device according to the invention, as mentioned above, can provide the gasoline engine compressed air for combustion already from the first revolution, which a traditional turbocharger can not. In an alternative embodiment, the device can direct compressed air into a memory, not shown, from which it can be supplied, for example, the individual cylinders of a motor.

Thus, a compression device is provided which is extremely efficient operable.

Claims

claims

Compression device with at least one, an inner wall (23) having cylinder (24) and in the cylinder (24) eccentrically to its longitudinal axis (25) rotatably mounted piston (26) having a circular cross-section (27), wherein the outer diameter (30 ) of the piston (26) for the formation of at least one compression space (31) is smaller than the inner cross section of the cylinder (24) and the piston (26) in sealing contact with the inner wall (23) of the cylinder (24) and one in the radial direction the piston (26) movable means (32) which is also in sealing contact with the inner wall (23) of the cylinder (24) and rotates with the piston (26).

2. Compression device according to claim 1, characterized in that in the radial direction of the piston (26) movable means (32) has two diametrically opposed wing parts (33, 34) which in each case radially outwardly biased on the inner wall (23). of the cylinder (24) abut.

3. A compression device according to claim 2, characterized in that the wing parts (33, 34) in the piston (26) guided by spring force and / or in the piston (26) provided connection channels using the compressed air or the compressed fuel / air mixture radially outwardly to the inner wall (23) of the cylinder (24) are charged towards.

Compression device according to one of Claims 1 to 3, characterized in that the cylinder (24) has inlet and outlet valves (51, 54, 77, 82; 22, 36) for the fluid or fluid mixture involved in the compression process and has a ( 82) of the intake valves compressed air and / or another (77) of the intake valves, a fuel / air mixture in the compression space (31) and a second cylinder chamber (60) can be introduced.

5. Compression device according to one of the preceding claims, characterized in that on the head sides (40, 41) of the cylinder (24) respectively a free-running seal plate (42) is arranged, which has on its side facing away from the piston (26) outside (43) grooves (44) for a lubricant.

6. Compression device according to claim 5, characterized in that the 5 grooves (44) at an acute angle (45) obliquely to the radial direction of

Seal plate (42) are arranged.

7. Compression device according to claim 5 or 6, characterized in that on the head sides (40, 41) of the cylinder (24) Cylinder head

I 0 cover plates (46, 47) with lubricant channels (50) are arranged such that the lubricant channels (50) in the region of the respective sealing plate (42) provided grooves (44) open.