NL2034024B1

NL2034024B1 - Rotary machine

Info

Publication number: NL2034024B1
Application number: NL2034024A
Authority: NL
Inventors: Theodorus Clemens Bekking Wilhelmus
Original assignee: Be Simplex B V
Priority date: 2023-01-26
Filing date: 2023-01-26
Publication date: 2024-08-13
Also published as: WO2024158282A1

Abstract

A rotary machine (1), comprising a housing (2a, 2h, 20) enclosing a disc shaped rotor (4a, 4b, 4c) rotatably mounted in the housing (2a, 2b, 2c) around a rotor axis (Y); a spherical chamber (3) 5 arranged in the housing (2a, 2b, 2c) enclosing a disc shaped joiner (5) rotatably mounted to the rotor (4a, 4b, 4c). The rotor (4a, 4b, 4c) and joiner (5) together partition the spherical chamber (3) into four subchambers for compression and decompression. The joiner (5) is rotatable around a disc axis (X) which is orthogonal to and rotatable around the rotor axis (Y) in unison with the rotor (4a, 4b, 4c). Ajoiner seal (9) is provided for engaging an inner surface part ofthe spherical 10 chamber (3) and wherein thejoiner seal (9) is arranged along a circumferential edge (7) of the joiner (5). [Figure 1]

Description

Rotary machine

Field of the invention

The present invention relates to a rotary machine, in particular a rotary machine for use in power generation and/or pumping applications, e.g. for the construction of turbines, pumps and motor-generators.

Background

International application WO 2012/002816 A2 discloses a rotary machine for compression and decompression, comprising a disc-shaped rotor having a first rotation axis at right angles to the plane of the rotor and situated in a plane of orientation and a disc-shaped swing element having a second rotation axis. In the orientation plane, the second rotation axis makes an angle with the first rotation axis. A spherical housing surrounds the rotor and the swing element and in combination form four (de)compression chambers. A connecting body positions the rotor and the swing element in the housing. The rotary machine further comprises a power drive and a mechanical connection delivering power to or taking off power from the rotary machine.

For prior art rotary machines of the type described above, reducing leakage and pressure loss by the four (de)compression chambers whilst maintaining low friction between various engaging surfaces remains a challenge. Therefore, there is a need for a rotary machine that exhibits minimal leakage and pressure loss whilst minimizing friction such that operating efficiency of the rotary machine is increased.

Summary

The present invention seeks to provide an improved rotary machine for power generation, pumping applications and the like, wherein the rotary machine is reliable, compact and exhibits improved efficiency. According to the present invention, a rotary machine of the type described above is provided, where the rotary machine comprises a housing enclosing a planar or disc shaped rotor rotatably mounted in the housing around a rotor axis having a fixed orientation with respect to the housing; a spherical chamber arranged in the housing and enclosing a circular or disc shaped joiner rotatably mounted to the rotor and extending therethrough, wherein the rotor and the joiner together partition the spherical chamber into four subchambers for compression and decompression, and wherein the joiner is rotatable around a disc axis which is orthogonal to and rotatable around the rotor axis in unison with the rotor, and wherein the joiner comprises two semi-circular joiner disc portions and a cylindrically shaped joiner cylinder, the two joiner disc portions being arranged on opposing sides of the joiner cylinder which extends along the disc axis, wherein the two joiner disc portions and the joiner cylinder form a single piece component; and wherein each of the two joiner disc portions comprises a circumferential edge and a guide slot extending there through;

a guide member mounted to the housing and extending along a swing axis which is arranged at a swing angle between 0° and 90° with respect to the rotor axis, wherein the swing axis has a fixed orientation with respect the housing, and wherein the guide member extends through the guide slot; and wherein the joiner further comprises a joiner seal for engaging an inner surface part of the spherical chamber and wherein the joiner seal is arranged along the circumferential edge of each of the two joiner disc portions.

According to the present invention, the joiner seal significantly reduces leakage along the two joiner disc portions and the inner surface part of the spherical chamber, thereby improving efficiency when the rotary machine is in operation.

In an embodiment, the joiner comprises two spherically shaped joiner cap seals arranged on opposing ends of the joiner cylinder, so that leakage along the opposing ends of the joiner cylinder is reduced.

In another embodiment, the rotor comprises two rotor beam seals extending along and on opposing sides of the joiner cylinder between the two joiner cap seals parallel to the disc axis. In this embodiment, the two rotor beam seals reduce leakage along the joiner cylinder and the rotor, thus further increasing efficiency of the rotary machine.

Short description of drawings

The present invention will be discussed in more detail below, with reference to the attached drawings, in which

Figure 1 depicts an exploded view of a rotary machine according to an embodiment of the present invention;

Figure 2 depicts an exploded view of a rotary machine according to another embodiment of the present invention;

Figure 3 shows a prior art swinger disc in movable engagement with a joiner cylinder;

Figure 4 shows a joiner as used in the rotary machine of the present invention;

Figure 5 shows a rotor beam seal extending along a joiner cylinder according to an embodiment of the present invention;

Figure 6 shows a one-way valve arranged in a partition piece of a rotor according to an embodiment of the present invention;

Figure 7 shows a roller member extending through a guide slot of a joiner disc portion according to an embodiment of the present invention;

Figure 8 shows a slider member according to an embodiment of the present invention;

Figure 9 shows a bearing cage comprising two spaced apart bearing rollers according to an embodiment of the present invention; and wherein

Figure 10 shows a cross sectional view of a housing and a rotor according to an embodiment of the present invention.

Detailed description of embodiments

Figure 1 and 2 each depict an exploded view of a rotary machine 1 according to an embodiment of the present invention. In the embodiments shown, the rotary machine 1, comprises a body or housing 2a, 2b, 2c enclosing a disc shaped or planar rotor 4a, 4b, 4c rotatably mounted in the housing 2a, 2b, 2c around a rotor axis Y, wherein the rotor axis Y has a fixed orientation with respect to the housing 2a, 2b, 2c. That is, the rotor 4a, 4b, 4c is arranged to rotate in the indicated direction R1 around the rotor axis Y in a rotation plane (not shown) perpendicular to the rotor axis Y.

In the exemplary embodiment as depicted, the housing 2a, 2b, 2c may comprise two opposing end parts 2a, 2b that are connected and spaced apart by a spacer part 2c arranged between the two end parts 2a, 2b.

The rotary machine 1 further comprises a spherical chamber 3 arranged in the housing 2a, 2b, 2c and encloses a circular or disc shaped “joiner” 5 rotatably mounted to the rotor 4a, 4b, 4c and wherein the joiner 5 extends through the planar rotor 4a, 4b, 4c. For simplicity and clarity, the joiner 5 may be seen as a substantially flat circular disc that is rotationally mounted to the rotor 4a, 4b, 4c and rotating therewith in unison around the rotor axis Y when the rotary machine 1 is in operation.

Regarding the spherical chamber 3, an embodiment of the spherical chamber 3 is depicted in Figure 10, showing a cross section of the housing and the rotor according to an embodiment. In Figure 10 the housing comprises two end parts 2a, 2b and a spacer part 2c there between. The rotor comprises two planar rotor parts 4a, 4b stacked together and wherein the rotor is rotatable around the rotor axis Y. The joiner 5 is not depicted. In Figure 10 it also seen that the housing and the rotor together may form or define the spherical chamber 3, and in particular, the two end parts 2a and the two rotor parts 4a, 4b may form or define the spherical chamber 3.

More details on the embodiment of Figure 10 will be discussed later.

The joiner 5 is rotatable around a disc axis X which is orthogonal to and rotatable around the rotor axis Y in unison with the rotor 4a, 4b, 4c. So when the rotary machine 1 in operation, the joiner 5 and disc axis X rotate around the rotor axis Y and as such it can be said that the disc axis

X rotates in a plane (not shown) perpendicular to the rotor axis Y. As will become clear later, the joiner 5 does not rotate around the disc axis X over a full rotation of 360° degrees. Instead, the joiner 5 oscillates around the disc axis X within an oscillation angle/range B as shown.

It is important to note that the rotor 4a, 4b, 4c and the joiner 5 together partition or delimit the spherical chamber 3 into four subchambers (not shown) for compression and decompression.

That is, the rotor 4a, 4b, 4c in conjunction with the joiner 5 partition the spherical chamber 3 into four quadrants seen as four subchambers. Each subchamber of the four subchambers defines a variable volume due to oscillatory behaviour of the joiner 5 around the disc axis X when the rotary machine 1 is in operation. In an exemplary embodiment and application, the four subchambers can be used to compress a combustible fuel and to let the combustible fuel expand the subchambers upon combustion, thereby forcing the rotor 4a, 4b, 4c to rotate and drive a generator-driver G as shown. In another embodiment and application, the rotor 4a, 4b, 4c may be driven by the generator-driver G for drawing in a fluid or gas into the rotary machine 1 when subchambers expand and to move the fluid or gas out of the rotary machine 1 when subchambers compress. In this way the rotary machine 1 acts as a pump.

To move a fluid or gas in and out of the rotary machine 1, an exemplary embodiment is depicted in Figure 10, wherein the housing 2a, 2b, 2c comprises a plurality of inlet/outlet ports P to allow a fluid or gas to enter and exit the housing 2a, 2b, 2c and to flow through one or more subchambers.

As mentioned, the joiner 5 may be seen as a substantially flat disc and comprises two semi-circular joiner disc portions 5a and a cylindrically shaped joiner cylinder 5b. The two joiner disc portions 5a are arranged on opposing sides of the joiner cylinder 5b which extends along the disc axis X. The two joiner disc portions 5a and the joiner cylinder 5b form a single piece component and as such are integrated into a single body.

Each of the two joiner disc portions 5a comprises a circumferential edge 7 and a guide slot 6 that extends there through. Note that guide slot 6 is in part delimited by the circumferential edge 7 on both sides of the guide slot 6. That is, the circumferential edge 7 may be viewed as at least an edge part of each joiner disc portion 5a defining opposing side walls of the joiner disc portions 5a between which the guide slot 6 extends. Note that in an embodiment the guide slot 6 may extend fully through the joiner 5 and thus fully through the two joiner disc portions 5a and the joiner cylinder 5b. Therefore, the guide slot 6 may be a blind slot having a bottom or the guide slot 6 may be an open slot fully extending through the joiner 5.

Regarding the four subchambers (not shown), in the embodiments of Figure 1 and 2, the rotor 4a, 4b, 4c may comprise two stacked planar rotor parts 4a, 4b having arranged there between two planar partition pieces 4c for arrangement on opposing sides of the joiner cylinder 5b, wherein each partition piece of the two planar partition pieces 4c separates two opposing subchambers (not shown) of the four subchambers. In particular, these two opposing subchambers may be seen as being separated in vertical direction as suggested in Figure 1 and 2, wherein a partition piece 4c acts like a horizontally arranged divider. Furthermore, each subchamber of the four subchambers is then delimited by a corresponding partition piece of the two partition pieces 4c and a corresponding joiner disc portion of the two joiner disc portions 5a.

The rotary machine 1 further comprises a guide member 8 mounted to the housing 2a, 2b, 2c and extends along a swing axis S which is arranged at a swing angle a between 0° and 90° degrees with respect to the rotor axis Y. The swing axis S has or maintains a fixed orientation with respect to the housing 2a, 2b, 2c and the guide member 8 extends into and through the guide slot 6 which is present along the circumferential edge 7. When the rotary machine 1 is in operation, the guide member 8 “forces” or imposes the joiner 5 to “swing” or oscillate in the indicated directions R2 over the swing angle a around the disc axis X when the rotor 4a, 4b, 4c rotates around the rotor axis Y during a full rotation of 360° degrees. As such the aforementioned oscillation angle/range B equals the swing angle a.

It is important to note that the abovementioned swing angle a is taken in absolute sense with respect to the rotor axis Y, so irrespective of whether the swing angle a is measured clockwise or counter clockwise. As such the swing angle a may likewise lie between 0° and -90° degrees. So when angle direction is taking into account, the swing angle a may be taken between -90° and +90° degrees.

To further clarify on how the joiner 5 moves when the rotary machine 1 is in operation, it 5 must be understood that the joiner 5 does not rotate around the swing axis S in regular sense, so where all points of the joiner 5 follow a circular orbit around swing axis S. For example, select an arbitrary point Q on a joiner disc portion 5a as shown in Figure 1, then this point Q will not follow a circular orbit around the swing axis S when the joiner 5 simultaneously rotates around the rotor axis Y and the disc axis X. Instead, this point Q will complete an orbit around the swing axis S, but this orbit is rather complex and goes beyond the scope which is relevant for the present invention.

In an exemplary embodiment, the swing angle a lies between e.g. 10° and 80°, e.g. between 20° and 70°, e.g. between 30° and 60°. The swing angle a can be chosen according to application requirements, e.g. the type of fuel chosen for generating power.

As shown in Figure 1, a joiner seal 9 is provided for engaging or bearing against an inner surface part of the spherical chamber 3 and wherein the joiner seal 9 is arranged along the circumferential edge 7 of each of the two joiner disc portions 5a. Advantageously, according to the invention, the joiner seal 9 prevents leakage along the circumferential edge 7 of each joiner disc portion 5a and as such prevents unwanted leakage between subchambers on opposing sides of each of the two joiner disc portions 5a.

The advantageous effects of the joiner seal 9 can be further explained by means of

Figures 3 and 4, wherein Figure 3 shows a prior art swinger disc D and a joiner cylinder 5b, and wherein Figure 4 shows a joiner 5 as used in the rotary machine 1 of the present invention.

In Figure 3, a guide member 8 comprises a swing disc D which is rotatable around the swing axis S, see rotation direction R3. The guide member 8 is mounted to the housing 2a, 2b, 2c and extends along the swing axis S. The swing disc D extends through the joiner cylinder 5b in slidable manner.

When the rotary machine 1 is in operation, the joiner cylinder 5b rotates in unison with the disc axis X around the rotor axis Y and the swing disc D rotates around the swing axis S. As shown in Figure 3, there is an edge interface L extending along the swing disc D and the joiner cylinder 5b. This edge interface L is difficult to seal against leakage due to e.g. the shape of the edge interface L as well as the sliding engagement between the swing disc D and the joiner cylinder 5b. To eliminate the edge interface L, the joiner 5 is provided as a single piece component comprising the joiner cylinder 5b and the two joiner disc portions 5a as shown in

Figure 4. As shown, the joiner 5 comprises the two semi-circular joiner disc portions 5a integrated with the joiner cylinder 5b as a single piece. Due to the single piece design of the joiner 5, the edge interface L depicted in Figure 3 is eliminated and moved toward the circumferential edge 7 of each of the two joiner disc portions 5a as shown in Figure 4. This newly positioned edge interface L along the circumferential edge 7 can now be sealed by means of the joiner seal 9 (not shown) as mentioned hereinbefore and shown in e.g. Figure 1. In the depicted embodiment, note that the guide member 8 comprises the swing disc D, wherein the guide member 8 and the swing disc D extend through the guide slot 6 as shown in Figure 2.

From Figure 3 and 4 it is clear that the rotary machine 1 of the present invention can be made more efficient and less prone to leakage by virtue of the elimination of the edge interface L as shown in Figure 3. The circumferential edge 7 now defines an edge interface L as shown in

Figure 4, and wherein the joiner seal 9 extends along the circumferential edge 7 of each of the two joiner disc portions 5a for sealing engagement with the inner surface part of the spherical chamber 3.

In an embodiment, the joiner seal 9 may extend along both sides of the guide slot 6, which is depicted in e.g. Figure 1, so that the joiner seal 9 provides two sealing engagements along the circumferential edge 7 on both side of the guide slot 6 for improved leak prevention.

As depicted in Figure 1, to further improve the efficiency of the rotary machine 1, an embodiment is provided wherein the joiner 5 further comprises two spherically shaped joiner cap seals 10 arranged on opposing ends of the joiner cylinder 5b. Here, both the joiner cap seals 10 are configured to engage the inner surface part of the spherical chamber 3 for preventing leakage along the opposing ends of the joiner cylinder 5b. The spherical shape of the joiner cap seals 10 provide a large sealing surface for excellent sealing properties.

Turning to Figure 5, there is shown an embodiment of a rotor beam seal 12 extending along the joiner cylinder 5b according to an embodiment of the present invention. In the depicted embodiment, the rotor 4a, 4b, 4c comprises two rotor beam seals 12 on opposing sides of the joiner cylinder 5b and extending there along between the two joiner cap seals 10 parallel to the disc axis X. In this embodiment, the two rotor beam seals 12 reduce leakage along the joiner cylinder 5b and the rotor 4a, 4b, 4c, thereby further increasing efficiency of the rotary machine 1.

In a further embodiment, each of the two rotor beam seals 12 comprises two spaced apart beam seal portions 12a extending parallel to each other along the joiner cylinder 5b. This provides for two separate sealing engagements with the joiner cylinder 5b by the rotor beam seal 12, thus further improving sealing performance of each of the two rotor beam seals 12.

From the embodiment in Figure 5 it can be seen that the joiner seal 9 extends toward the two opposing ends of the joiner cylinder 5b and engages the two joiner cap seals 10 at a first seal interface 11. In this embodiment, the joiner seal 9 and the two joiner cap seals 10 make contact and bear against each other so that leakage at the first seal interface 11 is prevented.

In Figure 5 a further embodiment is shown wherein the rotor 4a, 4b, 4c may comprise a rotor corner seal 13 at a second seal interface 14 between each corresponding engagement of a joiner cap seal of the two joiner cap seals 10 and a rotor beam seal of the two rotor beam seals 12. That is, in this embodiment each of the rotor beam seals 12 engages the two joiner cap seals 10 and at a second seal interface 14 between each rotor beam seal 12 and a corresponding joiner cap seal 10 there is provided a rotor corner seal 13. The rotor corner seal 13 further reduces leakage between the two rotor beam seals 12 and the two joiner cap seals 10, thereby further increasing operating efficiency of the rotary machine 1.

In a further embodiment, each rotor corner seal 13 may be arranged between two spaced apart beam seal portions 12a of a corresponding rotor beam seal 12 as shown in Figure 5. So at the second seal interface 14 there is a continued sealing engagement between a rotor beams seal 12, a rotor comer seal 13, and a joiner cap seal 10.

As mentioned earlier in light of Figure 10, the housing 2a, 2b, 2c may comprise a plurality of inlet and outlet ports P that are configured to allow a fluid or gas, such as a combustible fuel, to move through a subchamber of the four subchambers by virtue of compression and decompression of each of the four subchambers when the rotary machine 1 is in operation. The plurality of inlet and outlet ports P will be arranged in such a way that a required sequence of openings and closings of these inlet and outlet ports P is achieved when the rotor 4a, 4b, 4c and the joiner 5 rotate in unison around the rotor axis Y. The actual placements of the inlet and outlet ports P may depend of the type of fuel, the amount of power to be generated or what fluid or gas to pump, and so forth.

When each subchamber of the four subchambers is to be used for compression and combustion of a combustible fuel for power generation, then forced induction is used to forcibly supply a combustible fuel to each subchamber at an appropriate time during the compression and decompression cycle of each subchamber. In an exemplary application, forced induction may be achieved by one or more externally arranged turbochargers connected to inlet ports of the rotary machine 1. However, turbochargers are often complex, relatively expensive and prone to wear and even failure. As a result, there is a need to allow the rotary machine 1 to generate power through a natural aspiration process for fuel combustion, thereby eliminating the use of complex and expensive turbochargers for forced induction.

To allow the rotary machine 1 to operate through natural aspiration of a combustible fuel,

Figure 6 shows an embodiment of a one-way valve 18 arranged in a partition piece 4c of two partition pieces 4c. In particular, it was mentioned earlier that the rotor 4a, 4b, 4c may comprise two stacked planar rotor parts 4a, 4b, see Figure 1 and 2, having arranged there between two planar partition pieces 4c for arrangement on opposing sides of the joiner cylinder 5b. Each partition piece of the two planar partition pieces 4c separates, in part, two opposing subchambers of the four subchambers.

Figure 6 shows an embodiment of a one-way valve 18 arranged in a partition piece 4c of the rotor 4a, 4b, 4c of which only a single planar rotor part 4b is shown. Although not explicitly depicted, in an assembled state of the rotary machine 1 a first subchamber below the depicted partition piece 4c will be present and a second subchamber above the depicted partition piece 4c will be present. The one-way valve 18 in the partition piece 4c is then provided to allow these opposing first and second subchambers on either side of the partition piece 4c to communicate and exchange a fluid or gas, e.g. a combustible fuel.

To further explain the advantages of the one-way valve 18, in Figure 6 the first subchamber below the depicted partition piece 4c may be used to draw in a combustible fuel when this first subchamber expands whereby an under pressure is created such that the combustible fuel flows into the first subchamber. At some point during rotation of the rotor 4a, 4b,

4c, the first subchamber reduces in volume and compresses the drawn in combustible fuel upon which the one-way valve 18 allows the pressurized combustible fuel to flow into the second subchamber above the depicted partition piece 4c. This particular moment is in fact shown in

Figure 6, wherein the first subchamber below the depicted partition piece 4c is at its smallest and wherein the second subchamber above the depicted partition piece 4c is at its largest. The one- way valve 18 then allows the pressurized combustible fuel to move from the first subchamber to the second subchamber. Subsequently, when the rotor 4a, 4b, 4c continues to rotate around the rotor axis Y, this second subchamber that just received the combustible fuel via the one-way valve 18 starts to compress the combustible fuel by virtue of the one-way valve 18, i.e. the one-way valve 18 is configured to prohibit fuel/gas flow toward the first subchamber when the pressure increases in the second subchamber. When the second subchamber is near its smallest volume, the compressed combustible fuel can be ignited.

By taking the above into account, an embodiment is thus conceivable wherein the rotor 4a, 4b, 4c comprises two planar rotor parts 4a, 4b having arranged there between two planar partition pieces 4c for arrangement on opposing sides of the joiner cylinder 5b, and wherein each partition piece of the two partition pieces 4c separates two opposing subchambers of the four subchambers on opposing sides of the partition piece. Then, in an embodiment, each partition piece of the two partition pieces 4c comprises a one-way valve 18 for fluidly connecting the two opposing subchambers on opposing sides of the partition piece.

By utilizing a one-way valve 18 for each partition pieces 4c allows the rotary machine 1 to generate power without the need for forced induction (e.g. turbochargers). This will greatly simplify the engineering complexity of the rotary machine 1, lower cost thereof, and make the rotary machine1 more reliable. However, it is important to note that two subchambers of the fours chambers are used for drawing in combustible fuel and pushing this fuel through the one-way valves 18 toward the remaining two subchambers of the four subchambers. In turn, these remaining two subchambers compress the combustible fuel and expand upon combustion thereof.

Therefore, to achieve natural aspiration, two subchambers of the four subchambers are used to pressurize a combustible fuel and push the fuel to the remaining two subchambers by virtue of the one-way valve 18 in each partition piece 4c.

Referring to Figure 5 and 6, it can be further seen that the two planar partition pieces 4c may be used to hold the two rotor beam seals 12 in place, so that in an embodiment each of the two planar partition pieces 4c encloses a corresponding rotor beam seal of the two rotor beam seals 12. In this way the two rotor beam seals 12 can be accurately positioned for searingly engaging the joiner cylinder 5b. In a further embodiment, each of the two planar partition pieces 4c may also enclose two rotor corner seals 13 at the corresponding second seal interface 14, so that each of the partition pieces 4c allows for a reliable sealing engagement between each joiner cap seal 10 and a corresponding rotor corner seal 13.

Further measures can be taken to reduce leakage and improve efficiency of the rotary machine 1. For example, as depicted in Figure 5 and 6, in an embodiment each partition piece of the two partition pieces 4c may comprise a seal groove 16 on opposing sides of the partition piece, and wherein a body seal 15 is arranged in each seal groove 16 of the partition piece. The body seal 15 then extends between the two opposing joiner cap seals 10 in engagement therewith at a third seal interface 17 and wherein the body seal 15 further engages the housing 2a, 2b, 2c, e.g. a corresponding end part of the two end parts 2a, 2b of the housing 2a, 2b, 2c as mentioned earlier. In a further embodiment, the body seal 15 may comprise two opposing end portions 15a that extend beyond the third seal interface 17 along the two joiner cap seals 10. That is, both end portions 15a of the body seal 15 may extend along a corresponding joiner cap seal as shown in Figure 6 to achieve good and reliable sealing for improved operational efficiency of the rotary machine 1. 10 In an alternative embodiment (not shown), it is conceivable that the body seal 15 is formed as a single continuous seal ring that completely extends, e.g. a full 360° degrees, around the joiner cylinder 5b and as such extends through corresponding seal grooves 16 of the two partition pieces 4c. This also means that the body seal 15 completely extends along both opposing joiner cap seals 10 for optimal sealing properties.

In yet another alternative embodiment (not shown), it can be envisaged that the body seal 15 is arranged in the housing 2a, 2b, 2c for sealing the engagement between e.g. end parts 2a, 2b as mentioned earlier. In this alternative embodiment the two partition pieces 4c are not provided with seal grooves 16. Instead, the housing 2a, 2b, 2c is provided with appropriate seal grooves for receiving the body seal 15.

According to the present invention, various advantageous embodiments are conceivable for the guide member 8. For example, in Figure 7 a roller member 8a extending through a guide slot 6 of a joiner disc portion 5a according to an embodiment of the present invention is depicted.

In this embodiment the guide member 8 comprises a roller member 8a rotationally arranged around the swing axis S and wherein the roller member 8a extends through the guide slot 6 for rolling engagement with the circumferential edge 7, e.g. along side walls of the guide slot 6. So when the rotor 4a, 4b, 4c rotates around the rotor axis Y, the roller member 8a is able to roll through the guide slot 6 along the circumferential edge 7 when the joiner 5 rotates around the rotor axis Y and oscillates around the disc axis X. In an exemplary embodiment, the roller member 8a engages the circumferential edge 7 inside the guide slot 6 along a line parallel to the swing axis S in case the roller member 8a is a cylindrical roller member 8a.

Figure 8 shows a slider member 8b according to an alternative embodiment. In particular, in this embodiment the guide member 8 comprises a slider member 8b rotationally arranged around the swing axis S and wherein the slider member 8b extends through the guide slot 6 for sliding engagement with the circumferential edge 7, e.g. along side walls of the guide slot 6. This embodiment allows for a planar area of engagement in the guide slot 6 along the circumferential edge 7 as compared to the roller member 8a as shown in Figure 7. Such a planar area of engagement is able to provide a larger are for distributing forces along the circumferential edge 7 when the rotary machine 1 is in operation. During rotation of the rotor 4a, 4b, 4c, the slider member 8b slides through the guide slot 6 and simultaneously rotates around the swing axis S.

In a further embodiment, the slider member 8b may be curved and have a curvature C that is similar to a curvature of the circumferential edge 7. This allows the slider member 8b to be fully received in the guide slot 6 and provide a maximum planar engagement along the circumferential edge 7, e.g. along side walls of the guide slot 6.

Another alternative embodiment of the guide member 8 is shown in Figure 9, wherein the guide member 8 comprises a bearing cage 8c rotationally arranged around the swing axis S and extending through the guide slot 6, wherein the bearing cage 8c comprises two spaced apart bearing rollers 8d each of which is rotatable around a corresponding roller axis R. Each roller axis

R is arranged at an angle ö equal to or larger than 0° with respect to swing axis S, and wherein each of the two bearing rollers 8d is arranged for rolling engagement with the circumferential edge 7, e.g. along side walls of the guide slot 6. In this embodiment two offset bearing rollers 8d are provided each of which rotates around its own roller axis R. During rotation of the rotor 4a, 4b, 4c, the bearing cage 8c moves through the guide slot 6 and simultaneously rotates around the swing axis S. Each roller axis R is arranged at the angle ö to the swing axis S. By having two offset bearing rollers 8d, forces can be distributed over two positions along the circumferential edge 7, e.g. walls of the guide slot 6. In an exemplary embodiment, the angle ö of each roller axis R can be chosen such that both roller axes R cross each other at a centre point of the joiner 5. In a further embodiment, each bearing roller of the two bearing rollers 8d may be a cylindrical or conical bearing roller.

As with the slider member 8b of Figure 8, the bearing cage 8c may also have a curvature

C that is similar to a curvature of the circumferential edge 7, thereby allowing that the bearing cage 8c with the two bearing rollers 8d is fully received in the guide slot 6 for optimized rolling engagement along the circumferential edge 7, e.g. along side walls of the guide slot 6.

Referring to Figures 1 and 2, further details on alternative embodiments of the guide member 8 can be explained. First, in both Figures 1 and 2 the guide member 8 is mounted to the housing 2a, 2b, 2c and extends along the swing axis S and into the guide slot 6.

In Figure 1 it is shown that the guide member 8 is arranged on opposing sides of the joiner 5 and mounted to two end parts 2a, 2b of the housing 2a, 2b, 2c as discussed earlier.

Moreover, like Figure 9, the guide member 8 comprises the bearing cage 8c and two spaced apart bearing rollers 8d for rolling engagement with the circumferential edge 7, e.g. along side walls of the guide slot 6. In the embodiment the guide slot 6 is a blind slot comparable to a sufficiently deep groove in which the bearing cage 8c and the bearing rollers 8d can be fully received. Notably, the guide member 8 comprises two separate pieces, i.e. two opposing bearings cages 8c each with two bearing rollers 8d, on opposing sides of the joiner 5 and as such the guide member 8 does not fully extend through the joiner 5. Of course, in alternative embodiments, instead of the bearing cage 8c and bearing rollers 8d, the guide member 8 depicted in Figure 1 may just as well comprise two opposing roller members 8a as shown in Figure 7 or two opposing the slider member 8b. Mounting the guide member 8 on opposing sides of the joiner 5 in the housing 2a, 2b, 2c, allows forces to be evenly distributed on the joiner 5, thus providing even support to the joiner 5.

In Figure 2 the guide member 8 is also mounted to the housing 2a, 2b, 2c and extends along the swing axis S as depicted and into the guide slot 6. In the depicted embodiment the guide member 8 comprises the swing disc D which is rotationally arranged around the swing axis

S, see direction R3. The guide member 8 further comprises a guide shaft 8e mounted to the two end parts 2a, 2b of the housing 2a, 2b, 2c, and is journalled for rotation in the two end parts 2a, 2b on opposing sides of the joiner 5. The swing disc D is fixedly connected to this guide shaft 8e and slidably extends through the guide slot 6 that entirely extends through the joiner 5. Like the embodiment of Figure 1, mounting the guide member 8 on opposing sides of the joiner 5 in the housing 2a, 2b, 2b, allows forces to be evenly distributed on the joiner 5, thus providing even support to the joiner 5.

Contrary to the joiner 5, the swing disc D rotates around the swing axis S in regular sense, i.e. off-axis points of the swing disc D follow a circular orbit around the swing axis S. This is readily understood by observing that the guide shaft 8e and swing disc D are fixedly connected so that the swing disc D can only rotate around the swing axis S. Furthermore, the swing axis S has a fixed orientation with respect to the housing 2a, 2b, 2c and as such there is only a single rotational degree of freedom provided to the swing disc D, see direction R3.

It was mentioned earlier in light of Figures 1 and 2 that the housing 2a, 2b, 2c may comprise two opposing end parts 2a, 2b that are connected and spaced apart by a spacer part 2¢ arranged between the two end parts 2a, 2b. Figure 10 shows a cross sectional view of the housing 2a, 2b, 2c and the rotor 4a, 4b, in particular a stacked arrangement of two end parts 2a, 2b and a spacer part 2¢ enclosing two planar rotor parts 4a, 4b also stacked together. Note that the joiner 5 and the two partition pieces 4c are not depicted. As shown, in an embodiment the spherical chamber 3 may be formed by the two end parts 2a, 2b of the housing and the two planar rotor parts 4a, 4b of the rotor. Consequently, the joiner seal 9 which is arranged along the circumferential edge 7 of each of the two joiner disc portions 5a may engage the inner surface part of the spherical chamber 3 formed by the two end parts 2a, 2b and the two rotor parts 4a, 4b.

However, this also means that the joiner seal 9 may cross a seam point 19 where an end part 2a, 2b of the housing engages a corresponding rotor part 4a, 4b of the rotor. For example, Figure 10 shows a section (dotted) of a joiner seal 9 as well as a section (dotted) of a joiner cap seal 10 with respect of the spherical chamber 3. The joiner seal 9 then engages the joiner cap seal 10 at the first seal interface 11.

In this example it can be seen that the joiner seal 9 crosses the seam point 19 where the depicted upper end part 2a of the housing meets the upper rotor part 4a of the rotor. However, at the seam point 19 there may be an increased risk of leakage when the joiner seal 9 crosses between the upper end part 2a and the upper rotor part 4a. To reduce potential leaks at the seam point 19, the first seal interface 11 should remain positioned above the upper rotor part 4a for a full rotation of the rotor 4a, 4b around the rotor axis Y. This will ensure that the joiner seal 9 only engages the inner surface part of the spherical chamber 3 formed by the upper end part 2a of the housing.

The above observations can be further clarified by defining a rotor height h1 as measured from the disc axis X (e.g. half way point of the rotor) and by defining a seal interface height h2 of the first seal interface 11 as measured from the disc axis X. Here, the rotor height h1 is seen as the height of the rotor 4a, 4b as measured from the disc axis X to a circumferential portion of the rotor extending along the spherical chamber 3. Note that the seal interface height h2 will vary when the rotor 4a, 4b rotates around the rotor axis Y and the joiner 5 swings around the disc axis

X over the swing angle a.

Having defined the rotor height h1 and the seal interface height h2, an advantageous embodiment is now conceivable wherein the rotor height h1 of the rotor 4a, 4b, 4c as measured from the disc axis X is smaller than the seal interface height h2 of the first seal interface 11 as measured from the disc axis X, wherein the seal interface height h2 varies when the rotary machine 1 is in operation. So when h1 < h2, this embodiment ensures that the joiner seal 9 only engages the inner surface part of the spherical chamber 3 formed by the two end parts 2a, 2b.

Leakage of the joiner seal 9 is minimized as a result. Please be aware that Figure 10 depicts the case for h1 > h2 to show how the joiner seal 9 could cross the seam point 19.

In view of the above, the present invention can now be summarised by the following embodiments:

Embodiment 1: A rotary machine (1), comprising a housing (2a, 2b, 2¢) enclosing a disc shaped rotor (4a, 4b, 4c) rotatably mounted in the housing (2a, 2b, 2c) around a rotor axis (Y) having a fixed orientation with respect to the housing (2a, 2b, 2¢); a spherical chamber (3) arranged in the housing (2a, 2b, 2c) enclosing a disc shaped joiner (5) rotatably mounted to the rotor (4a, 4b, 4c) and extending therethrough, wherein the rotor (4a, 4b, 4c) and the joiner (5) together partition the spherical chamber (3) into four subchambers for compression and decompression, and wherein the joiner (5) is rotatable around a disc axis (X) which is orthogonal to and rotatable around the rotor axis (Y) in unison with the rotor (4a, 4b, 4c), and wherein the joiner (5) comprises two semi-circular joiner disc portions (5a) and a cylindrically shaped joiner cylinder (5b), the two joiner disc portions (5a) being arranged on opposing sides of the joiner cylinder (5b) which extends along the disc axis (X), wherein the two joiner disc portions (5a) and the joiner cylinder (5b) form a single piece component; and wherein each of the two joiner disc portions (5a) comprises a circumferential edge (7) and a guide slot (6) extending there through; a guide member (8) mounted to the housing (2a, 2b, 2c) and extending along a swing axis (S) arranged at a swing angle (a) between 0° and 90° with respect to the rotor axis (Y), the swing axis (S) having a fixed orientation with respect the housing (2a, 2b, 2c), and wherein the guide member (8) extends through the guide slot (6); and wherein the joiner (5) further comprises a joiner seal (9) for engaging an inner surface part of the spherical chamber (3) and wherein the joiner seal (9) is arranged along the circumferential edge (7) of each of the two joiner disc portions (5a).

Embodiment 2: The rotary machine according to embodiment 1, wherein the joiner (5) further comprises two spherically shaped joiner cap seals (10) arranged on opposing ends of the joiner cylinder (5b).

Embodiment 3: The rotary machine (1) according to embodiment 2, wherein the joiner seal (9) extends toward the opposing ends of the joiner cylinder (5b) engaging the two joiner cap seals (10) at a first seal interface (11).

Embodiment 4: The rotary machine (1) according to embodiment 3, wherein a rotor height (h1) of the rotor (4a, 4b, 4c) as measured from the disc axis (X) is smaller than a seal interface height (h2) of the first seal interface (11) as measured from the disc axis (X), wherein the seal interface height (h2) varies when the rotary machine (1) is in operation.

Embodiment 5: The rotary machine (1) according to any of embodiments 2-4, wherein the rotor (4a, 4b, 4c) comprises two rotor beam seals (12) extending along and on opposing sides of the joiner cylinder (5b) between the two joiner cap seals (10) parallel to the disc axis (X).

Embodiment 6: The rotary machine (1) according to embodiment 5, wherein each of the two rotor beam seals (12) comprises two spaced apart beam seal portions (12a) extending parallel to each other along the joiner cylinder (5b).

Embodiment 7: The rotary machine (1) according to embodiment 5 or 6, wherein the rotor (4a, 4b, 4c) comprises a rotor corner seal (13) at a second seal interface (14) between each corresponding engagement of a joiner cap seal of the two joiner cap seals (10) and a rotor beam seal of the two rotor beam seals (12).

Embodiment 8: The rotary machine (1) according to any of embodiments 1-7, wherein the rotor (4a, 4b, 4c) comprises two planar rotor parts (4a, 4b) having arranged there between two planar partition pieces (4c) for arrangement on opposing sides of the joiner cylinder (5b), wherein each partition piece of the two partition pieces (4c) separates two opposing subchambers of the four subchambers on opposing sides of the partition piece.

Embodiment 9: The rotary machine (1) according to embodiment 8, wherein each partition piece of the two partition pieces (4c) comprises a one-way valve (18) for fluidly connecting the two opposing subchambers on opposing sides of the partition piece.

Embodiment 10: The rotary machine (1) according to embodiment 8 or 9 and any of embodiments to 7, wherein each of the two partition pieces (4c) encloses a corresponding rotor beam seal of the two rotor beam seals (12). 5 Embodiment 11: The rotary machine (1) according to any of embodiments 8-10, wherein each partition piece of the two partition pieces (4c) comprises a seal groove (16) on opposing sides of the partition piece, and wherein a body seal (15) is arranged in each seal groove (16) of the partition piece and extends between the two opposing joiner cap seals (10) in engagement therewith at a third seal interface (17), and wherein the body seal (15) engages the housing (2a, 2b, 20).

Embodiment 12: The rotary machine (1) according to embodiment 11, wherein the body seal (15) comprises two opposing end portions (15a) extending beyond the third seal interface (17) along the two joiner cap seals (10).

Embodiment 13: The rotary machine (1) according to any of embodiments 1-12, wherein the guide member (8) comprises a roller member (8a) rotationally arranged around the swing axis (S) and wherein the roller member (8a) extends through the guide slot (6) for rolling engagement with the circumferential edge (7).

Embodiment 14: The rotary machine (1) according to any of embodiments 1-12, wherein the guide member (8) comprises a slider member (8b) rotationally arranged around the swing axis (S) and wherein the slider member (8b) extends through the guide slot (6) for sliding engagement with the circumferential edge (7).

Embodiment 15: The rotary machine (1) according to any of embodiments 1-12, wherein the guide member (8) comprises a bearing cage (8c) rotationally arranged round the swing axis (S) and extending through the guide slot (6) and comprises two spaced apart bearing rollers (8d) each of which is rotatable around a corresponding roller axis (R), wherein each roller axis (R) is arranged at an angle (5) equal to or larger than 0° with respect to swing axis (S), and wherein each of the two bearing rollers (8d) is arranged for rolling engagement with the circumferential edge (7).

In a further aspect, the present invention relates to a rotary machine 1 for power generation, in particular a natural aspiration rotary machine for power generation, comprising a housing 2a, 2b, 2c enclosing a disc shaped or planar rotor 4a, 4b, 4c rotatably mounted in the housing 2a, 2b, 2c around a rotor axis Y having a fixed orientation with respect to the housing 2a, 2b, 2¢; a spherical chamber 3 arranged in the housing 2a, 2b, 2c enclosing a circular or disc/planar shaped joiner 5 rotatably mounted to the rotor 4a, 4b, 4c and extending therethrough,

wherein the rotor 4a, 4b, 4c and the joiner 5 together partition the spherical chamber 3 into four subchambers for compression and decompression, and wherein the joiner 5 is rotatable around a disc axis X which is orthogonal to and rotatable around the rotor axis Y in unison with the rotor 4a, 4b, 4c, and wherein the joiner 5 comprises two semi-circular joiner disc portions 5a and a cylindrically shaped joiner cylinder 5b, the two joiner disc portions 5a being arranged on opposing sides of the joiner cylinder 5b which extends along the disc axis X, wherein the two joiner disc portions 5a and the joiner cylinder 5b form a single piece component; and wherein each of the two joiner disc portions 5a comprises a circumferential edge 7 and a guide slot 6 extending there through; a guide member 8 mounted to the housing 2a, 2b, 2c and extending along a swing axis

S arranged at a swing angle a between 0° and 90° with respect to the rotor axis Y, the swing axis

S having a fixed orientation with respect the housing 2a, 2b, 2c, and wherein the guide member 8 extends through the guide slot 6; and wherein the rotor 4a, 4b, 4c comprises two planar rotor parts 4a, 4b having arranged there between two planar partition pieces 4c for arrangement on opposing sides of the joiner cylinder 5b, wherein each partition piece of the two partition pieces 4c separates two opposing subchambers of the four subchambers on opposing sides of the partition piece, and wherein each partition piece of the two partition pieces 4c comprises a one-way valve 18 for fluidly connecting the two opposing subchambers on opposing sides of the partition piece.

By utilizing a one-way valve 18 for each of the two partition pieces 4c allows the rotary machine 1 to generate power without the need for forced induction to draw in a combustible fuel.

This will greatly simplify the engineering complexity of the rotary machine 1, lower cost thereof, and make the rotary machine 1 more reliable. The one-way valve 18 in each partition piece 4c allows two subchambers of the four subchambers to draw in a combustible fuel and supply the combustible fuel to the remaining two subchambers through the one-way valve 18.

Claims

CONCLUSIONS

1. A rotary machine (1), comprising a housing (2a, 2b, 2c) enclosing a disk-shaped rotor (4a, 4b, 4c) rotatably mounted in the housing (2a, 2b, 2c) about a rotor axis (Y) having a fixed orientation relative to the housing (2a, 2b, 2¢); a spherical chamber (3) disposed in the housing (2a, 2b, 2c) enclosing a disk-shaped connecting piece (5) rotatably mounted on the rotor (4a, 4b, 4c) and extending therethrough, the rotor (4a, 4b, 4c) and the connecting piece (5) together dividing the spherical chamber (3) into four sub-chambers for compression and decompression, and the connecting piece (5) is rotatable about a disk axis (X) perpendicular to and rotatable about the rotor axis (Y) together with the rotor (4a, 4b, 4c), and the connecting piece (5) comprises two semi-circular connecting disk portions (5a) and a cylindrically shaped connecting cylinder (5b), the two connecting disk portions (5a) being disposed on opposite sides of the connecting cylinder (5b) extending along the disk axis (X), the two connecting disk portions (5a) and the connecting cylinder (5b) forming a one-piece component; and wherein each of the two connecting disk portions (5a) includes a peripheral edge (7) and a guide slot (6) extending therethrough; a guide member (8) mounted on the housing (2a, 2b, 2¢) and extending along a pivot axis (S) disposed at a pivot angle (α) between 0° and 90° with respect to the rotor axis (Y), the pivot axis (S) having a fixed orientation with respect to the housing (2a, 2b, 2c), and wherein the guide member (8) extends through the guide slot (6); and wherein the connecting piece (5) further includes a connecting seal (9) for engaging an inner surface portion of the spherical chamber (3) and wherein the connecting seal (9) is disposed along the peripheral edge (7) of each of the two connecting disk portions (5a).

2. The rotary machine according to claim 1, wherein the connecting piece (5) further comprises two spherical connecting cap seals (10) provided on opposite ends of the connecting cylinder (5b).

3. The rotary machine (1) according to claim 2, wherein the connection seal (9) extends toward the opposite ends of the connection cylinder (5b} and engages the two connection cap seals (10) at a first sealing interface (11).

4. The rotary machine (1) according to claim 3, wherein a rotor height (h1) of the rotor (4a, 4b, 4c) as measured from the disk axis (X) is smaller than a sealing interface height (h2) of the first sealing interface (11) as measured from the disk axis (X}, the sealing interface height (h2) varying when the rotary machine (1) is in operation.

5. The rotary machine (1) according to any one of claims 2 to 4, wherein the rotor (4a, 4b, 4c) comprises two rotor bar seals (12) extending along and on opposite sides of the connecting cylinder (5b) between the two connecting cap seals (10) parallel to the disc axis (X).

6. The rotary machine (1) according to claim 5, wherein each of the two rotor bar seals (12) comprises two spaced apart bar seal portions (12a) extending parallel to each other along the connecting cylinder (5b).

7. The rotary machine (1) according to claim 5 or 6, wherein the rotor (4a, 4b, 4c) comprises a rotor corner seal (13) at a second sealing interface (14) between each corresponding engagement of a connection cap seal of the two connection cap seals (10) and a rotor bar seal of the two rotor bar seals (12).

8. The rotary machine (1) according to any one of claims 1 to 7, wherein the rotor (4a, 4b, 4c) comprises two planar rotor parts (4a, 4b) with two planar partitions (4c) disposed therebetween for disposition on opposite sides of the connecting cylinder (5b), each partition of the two partitions (4c) separating two opposite sub-chambers of the four sub-chambers on either side of the partition.

9. The rotary machine (1) according to claim 8, wherein each separator of the two separators (4c) comprises a one-way valve (18) for fluidly connecting the two opposing sub-chambers on either side of the separator.

10. The rotary machine (1) according to claim 8 or 9 and any one of claims 5 to 7, wherein each of the two separators (4c) encloses a corresponding rotor bar seal of the two rotor bar seals (12).

11. The rotary machine (1) according to any one of claims 8 to 10, wherein each separator of the two separators (4c) includes a seal groove (18) on opposite sides of the separator, and wherein a body seal (15) is provided in each seal groove (16) of the separator and extends between the two opposite connection cap seals (10) in engagement therewith at a third sealing interface (17), and wherein the body seal (15) engages the housing (2a, 2b, 2c).

12. The rotary machine (1) according to claim 11, wherein the body seal (15) comprises two opposite end portions (15a) extending beyond the third seal interface (17) along the two connecting cap seals (10).

The rotary machine (1) according to any one of claims 1 to 12, wherein the guide member (8) comprises a rolling member (8a) rotatably mounted about the pivot axis (S) and the rolling member (8a) extends through the guide slot (8) for rolling engagement with the peripheral edge (7).

The rotary machine (1) according to any one of claims 1 to 12, wherein the guide member (8) comprises a slide member (8b) rotatably mounted about the pivot axis (S) and the slide member (8b) extends through the guide slot (6) for sliding engagement with the peripheral edge (7).

15. The rotary machine (1) according to any one of claims 1 to 12, wherein the guide member (8) comprises a bearing cage (8c) rotatably mounted about the pivot axis (S) and extending through the guide slot (6) and comprises two spaced apart bearing rollers (8d) each rotatable about a corresponding roller axis (R), each roller axis (R) being disposed at an angle (3) equal to or greater than 0° with respect to the pivot axis (S), and each of the two bearing rollers (8d) being disposed for rolling engagement with the peripheral edge (7).