EP2655803B1 - Multi-stage or multi-channel pump, compressor or motor - Google Patents

Description

State of the art

The present invention relates to a rotary piston machine which operates as a pump, compressor or motor, with a rotor, an intermediate rotor and a counter-rotor.

From the DE 42 41 320 A1 is known a rotary piston machine, which works as a pump, compressor or motor. In this run combs of teeth of a rotating drive member for limiting work spaces on a cycloid surface of a likewise toothed output member and thereby drive this output member. Between the teeth of the driving part and the driven part, the said work spaces are formed, which are increased or reduced during the rotation of the parts for their work or to produce the conveying effect on a gaseous or liquid medium.

From the documents US 2002/0037228 . DE 10 2008 038 625 A1 and US 2,582,413 Similar rotary engines are known. At the US 2,582,413 However, the known number of teeth is the same, so that the working principle differs from that disclosed in the present application rotary piston engine.

Such drive and driven parts run in a common housing, whose interior is spherical. For mounting these parts, the housing is divided such that the separation plane contains the center of the spherical interior, so that a first housing part with a hemispherical interior with a first center and a second housing part with a hemispherical interior and a second center is formed. As a result, special attention is to be paid to the design of the parting surfaces of the two housing parts in such a way that in the assembled state the first and the second center of the spherical interior spaces of the housing parts coincide. Particular attention should be paid to the design of the housing separation surfaces with regard to the sealing technology to be used.

Summary of the invention

There may therefore be a need to provide a housing with an easy-to-manufacture interior.

This need can be solved by an article of the independent claim. Advantageous embodiments are specified in the dependent claims.

A rotary piston engine operating as a pump, compressor or motor includes a rotor, an intermediate rotor and a counter rotor with the intermediate rotor disposed between the rotor and the counter rotor. The counter rotor has a first end face with a first toothing. The intermediate rotor has a second end face with a second toothing and a third end face with a third toothing. The rotor has a fourth end face with a fourth toothing. Each toothing is formed from at least one tooth and one tooth gap. The teeth are engaged with each other such that first working spaces are formed by meshing the teeth of the first teeth and the teeth of the second teeth, and that second working spaces are formed by meshing the teeth of the third teeth and the teeth of the fourth teeth, wherein the first and second work spaces formed volumes are changed by the combing of the teeth. The rotors are rotatably guided in a housing accommodating the rotors. An inner wall of the housing is largely modeled on an outer contour of the rotors. The counter rotor has a first axis of rotation, the intermediate rotor a second axis of rotation and the rotor has a third axis of rotation, wherein the first axis of rotation and the second axis of rotation include a first angle and the second axis of rotation and the third axis of rotation a second angle. Here, the first and the second angle is not equal to 0 °. Furthermore, the rotor, the intermediate rotor and the counter rotor in a housing mounted position form a hemisphere stump.

Thus, it can be considered as an advantage of the invention that, since the inner wall of the housing largely follows the outer contour of the rotor, the intermediate rotor and the counter rotor in the assembled state, the inner wall of the housing, the rotor, the intermediate rotor and the Opposite rotor surrounds, is formed as a hemisphere. Thus, the housing can be made in one piece, wherein the processing for generating the inner wall can be made from one direction. Also, the assembly of rotor, intermediate rotor and counter rotor can be made from one direction. By these measures, on the one hand eliminates a split housing with the subsequent sealing problem with respect to the parting surfaces. On the other hand, by machining the interior from only one machining direction, precisely any gap between the rotors and the inner wall can be maintained. In particular, when using fast-running rotors in conjunction with a promotion of non-lubricating media, such a gap between the individual rotors and the inner wall is circumferentially maintained so that rotors and inner wall do not touch. Such contact could lead to damage to the rotors or inner wall or to overheating of the components due to friction. However, the gap should be as small as possible, since it can form a leak for the medium to be pumped and thus can adversely affect the efficiency of the rotary piston engine.

The term hemispherical stump is understood herein to mean that a ball is cut through a first plane and a second plane parallel to the first plane, the first plane containing the center of the ball and the second plane cutting off a ball cap. The term hemispherical stump should also be understood to mean a spherical segment in which the first plane does not contain the center of the sphere, but rather intersects the sphere at a point approximated to the second plane.

In the invention, the second toothing of the intermediate rotor has one tooth less than the first toothing of the counter-rotor. Furthermore, the second toothing and the third toothing of the intermediate rotor have the same number of teeth. The fourth toothing of the rotor has one tooth less than the third toothing of the intermediate rotor.

By this choice of teeth can be ensured that, on the one hand, the outer contour of the rotor, intermediate rotor and counter rotor is preserved in the form of a hemisphere stump and, secondly, that the first and second work spaces are as large as possible. Due to the largest possible design of the work spaces, a high throughput of the medium to be transported can be achieved with the rotary piston machine. It should also be noted that in the present embodiment, the pitch of the individual gears is the same. Due to the different number of teeth of the respective gears, the counter rotor rotate slower and the rotor faster than the intermediate rotor. Therefore, this embodiment of the rotary piston engine can also be used as a transmission.

In a further embodiment of the invention, the intermediate rotor is formed as a corrugated disk.

This wave-like formation is produced by a tooth gap of the third toothing protruding into a tooth root of the second toothing and vice versa. By this configuration, on the one hand material accumulations are avoided within the intermediate rotor and, on the other hand, the size of the work spaces is maximized.

In a further embodiment of the invention, the first working spaces formed between the first and second toothing have no connection to the second working spaces formed between the third and fourth toothing, so that the rotary piston machine can be operated in multiple stages and / or multiple-flow.

Multi-flow operation means that a medium to be transported is split into a first volume flow and a second volume flow, wherein the first volume flow is supplied to the first working spaces and the second volume flow to the second working spaces. As a rule, these two volume flows are brought together again after reaching the maximum pressure increase by the rotary piston engine at the outlet.

A multi-stage operation means that a volume flow is supplied to the first working spaces that control the pressure of the medium to be transported increase and then this pre-compressed medium to be transported is supplied to the second working spaces, which increase the pressure of the medium to be transported again.

In a further embodiment of the invention, the housing has an overflow chamber, which is set up in such a way that, during multistage operation, it receives the medium compressed by a first stage and supplies it to a second stage.

Here, the compressed by the first working spaces to be transported medium is stored in an overflow chamber. This overflow chamber may be attached to the housing as a separate chamber. The compression of the medium through the first working spaces can also be referred to as the first stage. From the overflow chamber, the second work spaces remove the already pre-compressed medium to be transported and compress it again. This further compression can be referred to as a second stage, so to speak. By adding further intermediate rotors, it is possible to further compress the medium to be transported.

In a further embodiment of the invention, the overflow chamber is formed as a recess on the inner wall of the housing.

This makes it possible to dispense with a separate chamber, which can be attached to the outside of the housing.

In a further embodiment of the invention, a drive device with a component from the group rotor, intermediate rotor and counter rotor and / or a driven device with another component from the group rotor, intermediate rotor and counter rotor is rotatably connected.

In such a constellation, the rotary piston engine can be used as a transmission, so that the drive device and the output device have different speeds. Furthermore, it is possible to use in a coupling of a drive device, such as a motor, the group rotor, intermediate rotor and counter rotor as a pump or compressor. Also, the group rotor, intermediate rotor and counter rotor, if this with a medium is driven, drive a driven device and act as a motor. Furthermore, by connecting the drive device to the rotor, the intermediate rotor or the counter rotor, it is possible to correspondingly influence the rotational speed of the rotary piston machine at a constant rotational speed of the drive device. In the present embodiment, the drive device is rotatably connected to the counter rotor.

In a further embodiment of the invention, the first angle and the second angle are oriented in the opposite direction.

By such an arrangement of the two angles, the individual rotors are adjusted to each other so that when the first working space is minimal, the two of these first working space directly adjacent second working spaces are maximum. This offers the advantage, in particular in multi-stage design, that the inflow and outflow channel can be arranged on the same side of the housing.

In a further embodiment of the invention, the first angle and the second angle are oriented in the same direction.

This embodiment appears to be more suitable for multi-flow designs. With such an angle configuration, the first and second working spaces are at a maximum on a first side of the housing. At this first side of the housing, the inlet channels for the medium to be transported are arranged. Diametrically opposite the inlet channels are on a second side of the housing outlet channels, since at this point the first and second working spaces are minimal and thus the medium to be transported has been subjected to the maximum pressure.

In a further embodiment of the invention, at least one component from the group housing, rotor, intermediate rotor (6) and counter rotor is integrally formed.

Due to the one-piece design, these parts are predestined to be manufactured as injection-molded parts. Here, the spray can be in both Plastic as well as metal take place. Thus, these components can be produced inexpensively with complex surface designs.

In a further embodiment of the invention at least two intermediate rotors can be arranged between the counter rotor and the rotor.

As a result, additional working spaces can be created, so that such a rotary engine designed can either compress a medium to be compressed even higher than is possible with a two-stage compression. Also in multi-flow operation, a higher volume flow can be enforced than would be possible with only one intermediate rotor. In addition, such a designed rotary piston machine can be operated both multi-flood and multi-stage,

In a further embodiment of the invention, at least one of the toothings (14, 18, 22, 26) is designed as a trochoid toothing.

In a further embodiment of the invention, the first axis of rotation and the third axis of rotation enclose a third angle which is not equal to 0 °.

It is noted that thoughts on the invention herein are described in the context of a rotary engine having a rotor, an intermediate rotor, and a counter rotor. It will be clear to a person skilled in the art that the individual features described can be combined with one another in various ways so as to arrive at other embodiments of the invention.

Embodiments of the invention will be described below with reference to the accompanying drawings. The figures are only schematic and not to scale.

Figur 1

zeigt eine erfindungsgemäße Drehkolbenmaschine im Querschnitt mit einer ersten Winkelanordnung der Rotorendrehachsen,

Figur 2

zeigt eine 3D-Ansicht von Rotorseite aus im Röntgenblick,

Figur 3

zeigt eine 3D-Ansciht der Rotoren im Arbeitsmodus für insbesondere mehrstufige Anwendung,

Figur 4

zeigt eine Explosionszeichnung der Rotoren aus Rotoransicht,

Figur 5

zeigt eine Explosionszeichnung der Rotoren aus Gegenrotorsicht,

Figur 6

zeigt eine Innenwandung eines Gehäuses für insbesondere mehrflutigen Betrieb und

Figur 7

zeigt eine erfindungsgemäße Drehkolbenmaschine im Querschnitt mit einer zweiten Winkelanordnung der Rotorendrehachsen.

Brief description of the drawings

FIG. 1

shows a rotary piston engine according to the invention in cross section with a first angular arrangement of the rotor rotational axes,

FIG. 2

shows a 3D view from the rotor side in the X-ray view,

FIG. 3

shows a 3D-Ansciht the rotors in the working mode for particular multi-stage application,

FIG. 4

shows an exploded view of the rotors from rotor view,

FIG. 5

shows an exploded view of the rotors from Gegenrotorsicht,

FIG. 6

shows an inner wall of a housing for in particular multi-flow operation and

FIG. 7

shows a rotary piston engine according to the invention in cross section with a second angular arrangement of the rotor axes of rotation.

Detailed description of exemplary embodiments

It should be said at this point that the same parts in the individual figures have the same reference numerals.

FIG. 1 shows a rotary piston machine 2 according to the invention in cross section, in particular for a multi-stage application. Here, a rotor 8, an intermediate rotor 6 and a counter rotor 4 is shown in working position. Here, the counter rotor 4 has on its first end face 12 a first toothing 14, which is formed from a first tooth 15. Furthermore, the intermediate rotor 6 has a second end face 16 facing the counter rotor 4, on which a second toothing 18, consisting of at least one second tooth 19, is formed. Furthermore, the intermediate rotor 6 has at a second end face 16 opposite the third end face 20, a third toothing 22, which is formed from a third tooth 23. Furthermore, the rotor 8 has a fourth end face 24 facing the third end face 20, on which a fourth toothing 26, consisting of at least one fourth tooth 27, is formed. Furthermore, it can be seen that the teeth 15, 19, 23 and 27 of the respective teeth 14, 18, 22 and 26 are engaged with each other such that by meshing the teeth 15 of the first teeth 14 and the teeth 19 of the second teeth 18 first Work spaces 28 are formed. Furthermore, by combing the teeth 23 of the third toothing 22 and the teeth 27 of the fourth toothing 26 second working spaces 30 are formed. The volumes formed by the first 28 and second working spaces 30 are changed by the meshing of the teeth 15, 19, 23 and 27. This is evident in the characters 2 and 8th seen. An inner wall 34 of the housing 32 follows an outer contour 36 of the rotors 4, 6, 8. It is clearly visible that the rotors 4, 6, 8 mounted in the housing 32 position form a half-cone stump. On one of the first end face 12 of the counter-rotor 4 opposite fifth end face 38 concentric with a cylindrical counter-rotor shaft 40 is formed. This counter rotor shaft 40 is in a first bearing 42 which is fixedly connected to the housing 32, stored. This first bearing 42 is a combined radial-axial bearing, on which axially the fifth end face 38 and radially of the counter rotor shaft 40 is supported. The counter rotor shaft 40 has a receptacle 44, by means of which a drive and / or driven device, not shown here, can be connected in a rotationally fixed manner to the counter rotor 4. Furthermore, a hemisphere 46 is concentrically arranged on the first end face 12 of the counter rotor 4. This hemisphere 46 is engaged with a spherical shaped support surface 48 disposed on the intermediate rotor 6. Further, the hemisphere 46 is engaged with a spherical shaped support surface 50 of the rotor 8. Thus, the intermediate rotor 6 and the rotor 8 can be deflected relative to the counter rotor 4 with respect to a center M of the hemisphere 46.

Opposite the fourth end face 24 is located on the rotor 8, a circular sixth end face 52, which constitute in conjunction with the first end face 12, the hemisphere stump bounding flat surfaces. At the sixth end face 52, a likewise cylindrical rotor shaft 54 is concentrically formed. This rotor shaft 54 in conjunction with the sixth end face 52 are supported on a combined axial-radial bearing 56. In the present embodiment, the counter rotor 4 rotates about a first axis of rotation I, the intermediate rotor 6 about a second axis of rotation II and the rotor 8 about a third axis of rotation III. The third axis of rotation III and the second axis of rotation II intersect at the center M of the hemisphere 46. A first angle φ1 is included between the first axis of rotation I. An angle φ2 is included between the second axis of rotation II and the third axis of rotation III. It can clearly be seen that the first angle φ1 and the second angle φ2 are oriented in the opposite direction. This is made clear by the two arrowheads 57. Furthermore, the first axis of rotation I and the third axis of rotation III enclose a third angle φ3, which is not equal to 0 °. As in FIG. 2 can be seen, results from this angular arrangement, a rotor assembly in which a first working space 28 with a maximum volume directly adjacent to two second work spaces 30 with a minimum volume. This is clearly visible in FIG. 2 ,

As continues in FIG. 2 it can be seen, on the housing 32, an inlet stub 58 is shown with an inlet control opening 64 formed in the inner wall 34 of the housing 32 as a recess. By means of the inlet stub 58, the working spaces 28 are supplied with the gaseous or liquid medium to be transported and / or compressed. The entirety of the first working spaces 28 is also referred to as the first stage. On the same side of the housing 32, an outlet port 60 is mounted, which is connected to a recess formed in the inner wall 34 of the housing 32 as a recess outlet control opening 66. The second working spaces 30 formed by the third toothing 22 and fourth toothing 26 may also be referred to as the second stage. Furthermore, the inlet 58 and outlet port 60 diametrically opposite in the inner wall 34 of the housing 32, a formed as a recess overflow chamber 62 can be seen (see also FIG. 6 ). It should also be noted that the inlet control port 64, the outlet control port 66 and the overflow chamber 62 have no fluid-communicating connections.

By rotating the counter-rotor 4, the intermediate rotor 6 and the rotor 8, the medium to be compressed, which may be liquid or gaseous, is sucked in via the inlet stub 58 and the inlet control opening 64 by means of the opening first working chambers 28. Anschießend the medium is compressed by the closing work spaces 28 and stored in this compressed state in the overflow 62. The medium in the overflow chamber thus has a higher pressure than at the inlet port 58 and has thus been compressed in a first stage. The compressed medium from the overflow chamber 62 is received by opening second working chambers 30 and then further compressed by closing second working spaces 30 and fed via the outlet control opening 66 to the outlet port 60. Here, the voltage applied to the outlet port 60 of the medium to be compressed is higher than in the overflow chamber 62. Thus, that is too compacting medium between inlet port 58 and outlet port 60 has been compressed two-stage.

FIG. 3 shows the two-stage compressor described above in working position, with only the counter rotor 4, the intermediate rotor 6 and the rotor 8 are shown. It can clearly be seen that a maximally opened first working space 28 faces a maximally closed second working space 30.

FIG. 4 shows an exploded view of the rotors 4, 6, 8 from the rotor sight. Clearly visible in the counter rotor 4 mounted hemisphere 46 can be seen on which the counter rotor 4 and the intermediate rotor 8 are supported. Furthermore, it can be seen that the first toothing 14 of the counter rotor 4 consists of eight first teeth 15. The second toothing 18 and the third toothing 22 of the intermediate rotor 6 are each formed from seven teeth 19 and 23. The fourth toothing 26 of the rotor 8 consists of six fourth teeth 27. Thus, the intermediate rotor 6 has a tooth 19, 23 less than the counter rotor 4 and the rotor 8 a tooth 27 less than the intermediate rotor 6. The intermediate rotor 6 is formed like a sheave, such in that a toothed space 10 of the third toothing 22 faces a second tooth 19 of the second toothing 18. Thus, no accumulations of material arise, as would happen if the second teeth 19 of the second toothing 18 would oppose the third teeth 23 of the third toothing 22.

FIG. 5 shows the representation of FIG. 4 , but seen from Gegenrotorsicht. Clearly visible here are the support surface 48 of the intermediate rotor 6 and the support surface 50 of the rotor 8.

FIG. 6 shows the inner wall 34 of the housing 32. Clearly in the inner wall 34, the recesses of the overflow chamber 62, the inlet control port 64 and the outlet control opening 66 can be seen.

FIG. 7 is different from the representation of FIG. 1 merely in that the first angle φ1 and the second angle φ2 are oriented in the same direction. This is indicated by the position of the arrowheads 57. Again, the enclosed between the first axis of rotation I and the third axis of rotation III third angle φ3 not equal to 0 °. Thus, the axis of rotation III relative to the axis of rotation I is stronger and deflected in the opposite direction than in FIG. 1 shown. This has the consequence that the first working space 28 with the largest volume two second work spaces 30 are directly adjacent, which also have the largest volume. Such an embodiment of the invention is particularly suitable for a multi-flow application.

As in FIG. 8 Visible, by means of the first stage formed by the first working space 28 through the inlet port 58, the liquid or gaseous medium to be transported is sucked in and fed to the inlet port 58 opposite outlet port 60 with pressure increase. On the same side of the housing 32, adjacent to the inlet port 58, there is another inlet port 68, through which the medium to be transported enters the second working spaces 30. Here, too, the medium to be transported is passed under pressure increase to a seated on the same side of the housing as the outlet 60 further outlet 70. Thus, a first volume flow of a medium to be transported between the inlet port 58 and the outlet port 60 is compressed and a second volume flow between the further inlet port 68 and the other outlet port 70th

Another advantage of the present invention is that at least one component from the group housing 32, rotor 8, intermediate rotor 6 and counter rotor 4 is integrally formed, so that it is predestined to be executed as an injection molded part made of either metal or plastic.

Claims (12)

1. Rotary piston machine which operates as a pump, compressor or motor,

   - having a rotor (8), having an intermediate rotor (6) and having a counter rotor (4), wherein the intermediate rotor (6) is arranged between the rotor (8) and the counter rotor (4),

   - wherein the counter rotor (4) has a first end face (12) with a first toothing (14), wherein the intermediate rotor (6) has a second end face (16) with a second toothing (18) and has a third end face (20) with a third toothing (22), and wherein the rotor (8) has a fourth end face (24) with a fourth toothing (26), and each toothing (14, 18, 22, 26) is formed from at least one tooth (15, 19, 23, 27) and one tooth space (10),

   - wherein the toothings (14, 18, 22, 26) engage with one another such that meshing of the teeth (15) of the first toothing (14) and of the teeth (19) of the second toothing (18) causes first working chambers (28) to be formed, and such that meshing of the teeth (23) of the third toothing (22) and of the teeth (27) of the fourth toothing (26) causes second working chambers (30) to be formed, wherein volumes formed by the first (28) and second working chambers (30) are varied by the meshing of the teeth (15, 19, 23, 27),

   - having a housing (32) with an inner wall (34), which housing accommodates the rotor (8), intermediate rotor (6) and counter rotor (4), wherein the rotor (8), intermediate rotor (6) and counter rotor (4) are guided rotatably in the housing (32), and the inner wall (34) largely follows an outer contour (36) of the rotor (8), intermediate rotor (6) and counter rotor (4),

   - wherein the counter rotor (4) has a first axis of rotation (I), wherein the intermediate rotor (6) has a second axis of rotation (II), wherein the rotor (8) has a third axis of rotation (III), wherein the first axis of rotation (I) and the second axis of rotation (II) enclose a first angle (ϕ₁), wherein the second axis of rotation (II) and the third axis of rotation (III) enclose a second angle (ϕ₂), and wherein the first (ϕ₁) and the second angle (ϕ₂) are not equal to 0°,

   characterized in that

   - the rotor (8), the intermediate rotor (6) and the counter rotor (4) form, in the position in which they are assembled in the housing, a hemispherical stump (36), wherein "hemispherical stump" is to be understood as meaning that a sphere is cut by a first plane and by a second plane which is parallel to the first plane, wherein the first plane contains the centre point and the second plane cuts away a spherical cap, or wherein the second plane cuts away a spherical cap and the first plane does not contain the centre point but rather cuts the sphere at a location closer to the second plane, and wherein an inner wall of the housing (32) substantially follows the outer contour of the rotor (8), the intermediate rotor (6) and the counter rotor (4) in the assembled state, and

   in that

   - the second toothing (18) has one tooth (19) fewer than the first toothing (14), in that the second toothing (18) and the third toothing (22) have the same number of teeth (19, 23), and in that the fourth toothing (26) has one tooth (27) fewer than the third toothing (22).
2. Rotary piston machine according to Claim 1, characterized in that the intermediate rotor (6) is in the form of an undulating disc.
3. Rotary piston machine according to one of the preceding claims, characterized in that the first working chambers (28) formed between the first (14) and second toothing (18) have no connection to the second working chambers (30) formed between the third (22) and fourth toothing (26), and so the rotary piston machine (2) is able to be operated in multi-stage and/or multi-channel configuration.
4. Rotary piston machine according to Claim 3, characterized in that the housing (32) has an overflow chamber (62) which is designed such that, during multi-stage operation, it receives the medium compressed by a first stage and supplies said medium to a second stage.
5. Rotary piston machine according to Claim 4, characterized in that the overflow chamber (62) is formed as a depression at the inner wall (34) of the housing (32).
6. Rotary piston machine according to one of the preceding claims, characterized in that a drive device is connected rotationally conjointly to a component from the group of rotor (8), intermediate rotor (6) and counter rotor (4), and/or an output device is connected rotationally conjointly to some other component from the group of rotor (8), intermediate rotor (6) and counter rotor (4).
7. Rotary piston machine according to one of the preceding claims, characterized in that the first angle (ϕ₁) and the second angle (ϕ₂) are oriented in opposite directions.
8. Rotary piston machine according to one of Claims 1 to 6, characterized in that the first angle (ϕ₁) and the second angle (ϕ₂) are oriented in the same direction.
9. Rotary piston machine according to one of the preceding claims, characterized in that at least one component from the group of housing (32), rotor (8), intermediate rotor (6) and counter rotor (4) is formed in one piece.
10. Rotary piston machine according to one of the preceding claims, characterized in that at least two intermediate rotors (6) are able to be arranged between the counter rotor (4) and the rotor (8).
11. Rotary piston machine according to one of the preceding claims, characterized in that at least one of the toothings (14, 18, 22, 26) is formed as a trochoidal toothing.
12. Rotary piston machine according to one of the preceding claims, characterized in that the first axis of rotation (I) and the third axis of rotation (III) enclose a third angle (ϕ₃) which is not equal to 0°.

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