Key information

Title
Positive displacement rotary machine
Application number
20220490
Case type
National
Status
22.12.2025 Patent meddelt (B1)
Filed
29.04.2022
Effective date
29.04.2022
Publicly available
30.10.2023
Next annual fee due
30.04.2027
Applicant
Tocircle Industries AS (NO)
Owner
ETNIR AS (NO)
Inventor
Nikolai Slettebø (NO)
Agent
BRYN AARFLOT AS (NO)
Granted
22.12.2025
Patent number
349378
Expiry date
29.04.2042

Abstract and drawing

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content.
A rotary machine for fluid processing, comprising a static casing (2) with a first and second port (H, L) for allowing fluid out of and into the rotary machine. The rotary machine comprises a rotor body (4, 4’) attached to a main shaft (3) arranged within the static casing (2),the rotor body (4, 4’) has a center axis (R) arranged an offset distance (e) from a center axis (M) of the main shaft (3), the rotary machine further comprising a sealing vane (5, 5’) having a vane tip (6, 6’), and a vane moving system (8, 8’) operationally connected between the rotor body (4) and the sealing vane (5, 5’) for maintaining a vane tip seal face (6a, 6c) of the vane tip (6, 6‘)in a sealing proximity to the rotor body outer face (4a, 4b).

Publications

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Documents

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Date
 Date Doc. No. Process Case number In/Out Journal description To/from
 23.10.2026 02-01 Overdragelse av søknad/rettighet 2026/07916 UT Tilbakemelding på generell henvendelse BRYN AARFLOT AS
 14.10.2026 01-02 Overdragelse av søknad/rettighet 2026/07916 INN GPOA NO Etnir AS BRYN AARFLOT AS
 14.10.2026 01-01 Overdragelse av søknad/rettighet 2026/07916 INN Generell henvendelse BRYN AARFLOT AS
 02.01.2026 12-01 Saksbehandling 20220490(349378) UT PT Registreringsbrev nasjonal patent (15) (PT20220490)
21.10.2025 11-01 Saksbehandling 20220490 UT Intention to grant BRYN AARFLOT AS
 02.10.2025 10-01 Saksbehandling 20220490 INN Korrespondanse (Hovedbrev inn) BRYN AARFLOT AS
 27.08.2024 09-09 Saksbehandling 20220490 INN P6467NO00 Response to Written Opinion filed 15 Feb 2024 BRYN AARFLOT AS
 27.08.2024 09-08 Saksbehandling 20220490 INN P6467NO00 Letter to NIPO 27Aug2024 BRYN AARFLOT AS
 27.08.2024 09-07 Saksbehandling 20220490 INN P6467NO00 Corrected drawings BRYN AARFLOT AS
 27.08.2024 09-06 Saksbehandling 20220490 INN P6467NO00 Amended Norwegian translation of the claims BRYN AARFLOT AS
 27.08.2024 09-05 Saksbehandling 20220490 INN P6467NO00 Amended description without annotations BRYN AARFLOT AS
 27.08.2024 09-04 Saksbehandling 20220490 INN P6467NO00 Amended description with annotations BRYN AARFLOT AS
 27.08.2024 09-03 Saksbehandling 20220490 INN P6467NO00 Amended claims without annotations BRYN AARFLOT AS
 27.08.2024 09-02 Saksbehandling 20220490 INN P6467NO00 Amended claims with annotations BRYN AARFLOT AS
 27.08.2024 09-01 Saksbehandling 20220490 INN Korrespondanse (Hovedbrev inn) BRYN AARFLOT AS
 30.04.2024 08-02 Saksbehandling 20220490 UT PT report 03:00:19
30.04.2024 08-01 Saksbehandling 20220490 UT Substantive examination BRYN AARFLOT AS
 26.02.2024 07-01 Saksbehandling 20220490 UT PT Varsel om betaling av første årsavgift (3317) (PT20220490) BRYN AARFLOT AS
 24.05.2023 06-07 Saksbehandling 20220490 INN Response NIPO BRYN AARFLOT AS
 24.05.2023 06-06 Saksbehandling 20220490 INN Norwegian translation of claims BRYN AARFLOT AS
 24.05.2023 06-05 Saksbehandling 20220490 INN Description - marked-up BRYN AARFLOT AS
 24.05.2023 06-04 Saksbehandling 20220490 INN Description - clean BRYN AARFLOT AS
 24.05.2023 06-03 Saksbehandling 20220490 INN Claims - marked-up BRYN AARFLOT AS
 24.05.2023 06-02 Saksbehandling 20220490 INN Claims - clean BRYN AARFLOT AS
 24.05.2023 06-01 Saksbehandling 20220490 INN Korrespondanse (Hovedbrev inn) BRYN AARFLOT AS
 29.11.2022 05-02 Saksbehandling 20220490 UT PT report 11:23:57
29.11.2022 05-01 Saksbehandling 20220490 UT Substantive examination PROTECTOR IP AS
 12.05.2022 04-01 Saksbehandling 20220490 UT Informasjon til oppfinner Nikolai Slettebø
 10.05.2022 03-01 Saksbehandling 20220490 INN Korrespondanse (Hovedbrev inn) PROTECTOR IP AS
 03.05.2022 02-01 Saksbehandling 20220490 UT Formal Examination 1 PROTECTOR IP AS
 29.04.2022 01-07 Saksbehandling 20220490 INN Generalfullmakt NO PROTECTOR IP AS
 29.04.2022 01-06 Saksbehandling 20220490 INN Figures PROTECTOR IP AS
 29.04.2022 01-05 Saksbehandling 20220490 INN Erklæring om retten til oppfinnelsen PROTECTOR IP AS
 29.04.2022 01-04 Saksbehandling 20220490 INN Description PROTECTOR IP AS
 29.04.2022 01-03 Saksbehandling 20220490 INN Claims PROTECTOR IP AS
 29.04.2022 01-02 Saksbehandling 20220490 INN Abstract PROTECTOR IP AS
 29.04.2022 01-01 Saksbehandling 20220490 INN Søknadsskjema Patent PROTECTOR IP AS

Description, claims and drawings

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content. Description
3493781POSITIVE DISPLACEMENT ROTARY MACHINETechnical FieldThe invention relates to a positive displacement rotary machine. Preferably, the positive displacement rotary machine is intended to be used as a compressor and/or 5 expander for gases or gas/liquid mixtures, or as a pump and/or hydromotor for liquids.Background ArtRotary machines with an eccentric rotor rotating around the centre axis of a10 cylindrical casing are well known and widely applied as, e.g., compressors in heating and cooling processes. In rotary machines of this type, a closed working chamber is formed between the three main parts; a static casing with a substantially cylindrical inner bore, a rotor, also cylindrical and with a diameter smaller than the casing bore, eccentrically fixed to a shaft rotatable around the casing bore centre in such a way 15 that the rotor outer wall tangents the casing inner wall, and a movable member or vane sealing between the casing and rotor. Each part must seal towards the two other parts to form a closed working chamber between them, and as the rotor rotates, the working chamber changes volume to compress or expand the processed working fluid20 Such machines are generally regarded as reliable and robust equipment, but mostly relies on a direct contact between the rotor and a sealing vane to provide sufficient sealing of the working chamber. This contact causes friction and sets a limit to the size and volumetric capacity of the machine or makes it necessary to introduce a lubricant directly into the working chamber or in the working fluid.25 Examples of prior art are:GB273439, which shows a rotor with an eccentric rotational axis. A wing lies with a tip against the outer surface of the rotor. There is a longitudinal seal on the rotor, which seals against the housing. A crank mechanism moves the wing.GB600383 describes a rotation machine comprising a static casing and a rotor body.30 The main shaft has a rotational axis that is coincident with a centra axis of a casing 3493782bore, and the rotor body has a geometric center axis that is offset from the main axis. It also shows a sealing vane and a vane moving system. Although not specifically stated, it is evident that the rotor body has two different circular cylinder segments. GB600383 has a sharp vane tip and clearly warns against rounding this tip. Hence 5 the contact between the tip and the rotor surface is along a very narrow line. Such a small contact area will inevitably cause great wear on the tip and leakage past the tip. CH504612 shows a vane tip with a semi-circular shape. However, the vane s forcedly moved by the direct contact with the surface of the rotor. This way of controlling the position of the vane puts substantial limitations of the capacity of the 10 machine. The vane must be biased against the rotor by a sufficient force. If this force is too low, the vane may jump on the rotor, especially when the rotational speed increases. Such jumping causes leakage between the rotor and the vane, and the efficiency of the machine is reduced.A greater biasing force will create larger friction and hence greater wear. The faster 15 the rotational speed of the machine is, the greater the biasing force must be, and the more wear will be caused; both because of the high friction and the high speed.The machine of CH504612 will therefore be suitable only for low-efficiency machines and machines where a lubricant can be added to the medium going through the machine.20 US3081707, US922189, US2005/0000214 and NO744622 also show a rotary machine according to similar principles.The present invention is advantageous (at least) in that it provides a way for the parts forming the working chamber to always remain in sealing proximity throughout the working cycle without the need for contact between them. Parts in sealing proximity 25 is to be understood as parts being in light or no contact but still forming no gap between them or a small enough gap to prevent excessive leakage of fluid in the gap. Hence there is no friction between these parts and no need to introduce lubricant into the working chamber. The three parts forming the working chamber is a static casing, a rotating rotor, and an oscillating vane. Both the rotor and the30 oscillating vane are fixed to shafts, and a conrod connects these shafts to control the oscillating movement of the vane. Geometric relations between the parts ensures 3493783that the curved faces of the stator, rotor and vane will tangent each other and seal the working chamber.A further advantage of the present invention is that the two mentioned shafts can easily be sealed around by conventional shaft seals, thus effectively isolating all 5 bearing functions from the working chamber, allowing lubrication of the bearings while keeping the working chamber free from lubricantThe invention is further advantageous in that it provides a method of contact-free and adjustable support of the vanes oscillating motion relative to the casing, that increases the control of the vane position and reduces the forces on the conrod and 10 the conrod bearingsFurther and other objects of the invention may be apparent by the following description and drawings.Summary of invention15 The invention relates to a rotary machine for fluid processing, comprising a static casing with a first and second port for allowing fluid out of and into the rotary machine,a rotor body attached to a main shaft arranged within the static casing, the rotor body has a center axis arranged an offset distance from a center axis of the main shaft. 20 The rotary machine further comprising a sealing vane having a vane tip, and a vane moving system operationally connected between the rotor body and the sealing vane for maintaining a vane tip seal face of the vane tip in a sealing proximity to the rotor body outer face. According to the invention, the rotor body has a lens-shaped cross section with two different cylinder segments, a first segment with an outer surface 25 having a center axis offset from the main shaft center axis by the offset distance, to form a seal against the vane tip seal face, and a second segment with an outer face concentric to and co-radial with the casing inner wall to seal against the casing inner wall at all positions of the rotor body.The invention relates to a rotary machine for fluid processing, comprising a static 30 casing with a first port and a second port for allowing fluid out of and into the rotary machine; the rotary machine comprising a rotor body, said rotor body having a rotor 3493784body outer face, said rotor body being attached to a main shaft, said main shaft being arranged within said static casing; said main shaft having a rotational centre axis which is coincident with a centre axis of a casing bore in said static casing; said rotor body having a first geometric center arranged an offset distance from said rotational 5 center axis of said main shaft; the rotary machine further comprising a sealing vane having a vane tip; and a vane moving system operationally connected between said rotor body and said sealing vane for maintaining a vane tip seal face of said vane tip in a sealing relationship with said rotor body; said vane moving system comprising at least one connecting rod operationally connected at a first end to said rotor body; 10 said at least one connecting rod being connected to a crank portion on said main shaft.The invention distinguishes from prior art by two alternative vane designs:- in a first alternative, said rotor body having a cross section with two different circular cylinder segments, a first segment with an outer surface having a geometric 15 center coinciding with said first geometric centre, and a second segment with an outer surface having a second geometric centre coinciding with said rotational centre axis, and said second segment outer surface being concentric to and co-radial with said casing bore to seal against a casing inner wall of said bore at all rotational positions of said rotor body; said crank portion being concentric with said first 20 segment outer surface of said rotor body; said vane tip seal face having a radius; said connecting rod at a second end thereof being operationally connected to a pivot arm at a cross pin thereof; said pivot arm being rigidly connected to said vane; said cross pin being concentric with said semi-circular face of said vane tip, and a length of said connecting rod between the center axes of said crank portion and said cross 25 pin being equal to a radius of said first segment outer surface plus the radius of the vane tip; or- in a second alternative, said vane tip comprising a vane tip element that is rotatable relative to said vane, said vane tip element having a first semi-circular cylindrical face that is concentric with an axis of rotation between said vane tip 30 element and said vane, said vane tip element being fixedly connected to said connecting rod, said vane tip element having a second semi-circular cylindrical seal face that is concentric and co-radial with the rotor body outer face. 3493785Preferable embodiments are set out in the accompanying dependent claims.Brief description of drawingsFigure 1 shows a cross sectional view of a rotary machine, illustrating a vane 5 according to the first alternative, viewed from the end,Figure 2 shows a cross sectional view of the rotary machine from figure1, viewed from the side,Figure 3 shows the rotary machine from figure 1, viewed from the outside, Figure 4 shows a rotary machine with a rotor body according to the invention, 10 Figure 5 shows a cross sectional view of a rotary machine, illustrating a vane according to the second alternative, viewed from the end,Figure 6 shows a cross sectional view of the rotary machine of figure 5, viewed from the side,Figure 7 shows the rotary machine of figure 5, viewed from the outside,15 Figure 8 shows a detailed view of an integrated vane support mechanism of the sealing vane.Detailed description of the inventionFor simplicity, equal features have been referred to by equal reference numbers in 20 the different figures.Figure 1 shows a cross section of a positive displacement rotary machine 1 having a van according to the first alternative.The rotary machine 1 comprises an outer casing 2 with a cylindrical inner wall 2a. The outer casing 2 having a first port L and a second port H. The first and second 25 port L, H are adapted to let a working fluid F into and out of the casing 2. The direction of the fluid F through each port L, H depends on the use of the rotary machine 1. The reference number 18 refers to a valve arrangement that is arranged in association with the port H to let the working fluid into or out of the casing 2. 3493786The rotary machine 1 further comprises a main shaft 3 rotatably supported in the outer casing 2. The main shaft 3 is concentrically arranged within a casing bore 1a. The casing bore 1a is defined as the bore within the outer casing 2. The outer boundary of the casing bore 1a is the same as the cylindrical inner wall 2a. A centre 5 axis M (fig 2) through the main shaft 3 is thus coincident with the centre axis M of the casing bore 1a. The centre axis M has a distance h to the cylindrical inner wall 2a. A rotor body 4 is further attached to the main shaft 3.As shown in figure 1, the rotor body outer surface 4a is mainly cylindrical, with its geometric centre R parallel to and offset from a rotational axis M. A radius r of the 10 rotor body outer surface 4a and the rotor offset e, is determined so that the part of the rotor body outer surface 4a furthest away from the rotational centre axis M is always in proximity to the casing inner wall 2a. This will create a seal between the casing inner wall 2a, and the rotor body outer surface 4a, without the rotor body 4 necessarily contacting the casing 2. This further results in that any friction between 15 the rotor body 4 and the casing 2 may be avoided. The rotary machine 1 further comprises a sealing vane 5. The sealing vane 5 is pivotably supported in the casing 2, by means of a vane shaft 7. The vane shaft 7 has a pivot axis V (see figure 2) that is parallel to and spaced apart from the rotational centre axis M of the main shaft 3. The sealing vane 5 comprises a vane tip 6 arranged at the free end of the sealing 20 vane 5, i.e., at the opposite end of the pivot axis V. The vane tip 6 may have a semicylindrical outer surface 6a. The sealing vane 5 is further arranged in the static casing 2 so that a vane tip outer surface 6a (see figure 8) is always in sealing proximity to the rotor body outer surface 4a, hence forming a seal between the rotor body 4 and the vane 5. This is further illustrated in figure 1.25 The sealing vane 5 also has a sealing face 5a. The sealing face 5a has a semicircular shape with its centre axis colinear with the centre axis V of the vane pivot axis. The sealing face 5a seals against a part 2b of the casing 2, effectively between the first and second port L, H.Thus, a closed working chamber W is formed between the rotor body 4, the casing 30 inner wall 2a and the vane 5. The volume of this working chamber W will increase or decrease as the rotor body 4 rotates, depending on the rotational direction, resulting in compression or expansion of the working fluid F. 3493787An embodiment, shown in Figure 4, of the rotary machine 50, shows a different configuration of a rotor body 4’. In this embodiment the rotor body 4’ does not have a cylindrical outer surface 4a. Instead, the rotor body has an approximately lensshaped cross section. The shape comprises two different circular cylinder segments.5 The shape comprises a first segment with an outer surface 4b having its geometric centre R offset from the rotational centre axis M by a distance ‘rotor offset’ e, to form a seal against the sealing vane tip 6a. The rotor body further comprises a second segment with an outer face 4c concentric to and co-radial with the casing inner wall 2a to seal against the casing inner wall 2a.10 The rotary machine 1 may further comprise a vane moving system 8. A first embodiment of this is illustrated in figure 2 and 3. The vane moving system 8 comprises one or more connecting rods 9. Each connecting rod 9 connecting the pivoting sealing vane 5 to a crank 10, via a pivot arm 11. The pivot arm 11 is rigidly mounted to the vane 5 in one end.15 The pivot arm 11 and the connecting rod 9 are rotationally connected to each other in respective ends via a cross pin 12, as shown in the figure 2.The connecting rod 9 is further in the opposite end rotationally connected to the crank 10.The crank 10 may as the figure 2 and 3 shows, be an integrated part of the main 20 shaft 3. However, the center axis of the crank 10 is arranged offset of the rotational centre axis M of the main shaft 3. This result in an offset rotation of the crank 10 and a consequent linear motion of the connecting rod 9 when the main shaft 3 rotates. The crank offset distance is the same distance e as the distance between the centre axis of the main shaft M and the centre axis of the rotor body R.25 The offset of the crank 10 being equal to the offset of the rotor body 4. This means that the geometrical center of the rotor body R and the center axis of the crank 10 being coincident.Figure 1 to 4 shows one embodiment of the vane moving system 8 in which the cross pin 12 linking the connecting rod 9 to the pivot arm 11 is concentric with the semi-30 circular cylindrical shape of the vane tip sealing face 6a. The length P of the connecting rod 9 also being equal to the sum of the length of the rotor body radius r 3493788and the vane tip radius v (fig.1). The length P is defined as the distance between the geometrical center R and the axis C of the cross-pin 12. Thus, the connecting rod 9 will guide the pivoting sealing vane 5 so that the vane tip 6a is always tangent to the rotor body outer face 4a, creating a sealing line S (illustrated in fig 8) without the 5 need for contact between the parts, i.e., rotor body 4 and the sealing vane tip 6a.This results in that no friction will occur between the vane tip 6a and the rotor body outer face 4a.More precisely, the semi-circular cylindrical face of the vane tip 6a is always tangent to the cylindrical rotor body outer face 4a.10 Figure 5 to 7 shows another embodiment of a sealing vane 5’ and vane moving system 8’ according to the invention.In the embodiment the rotary machine 60 in figure 5-7 a vane tip 6’ element is rigidly connected to the connecting rod 9’. The vane tip 6’ element has a first semi-circular face 6b sealing against the vane 5’, and a second semi-circular face 6c sealing 15 against the rotor body outer face 4a. As the figure 5 shows, the first semi-circular face 6b is adapted to mate with a vane semi-circular face 5b of the vane 5’. Similarly, the second semi-circular face 6c is adapted to mate with the circular shape of the rotor body outer face 4a.The vane tip 6’ is connected to the vane 5’ by the vane tip bearing 17 (fig.6),20 ensuring that the vane 5’ will follow the motion of the vane tip 6’. This embodiment has the advantage that the vane tip second sealing face 6c may be both concentric and co-radial as the rotor body outer face 4a. This provides a better seal between the second sealing face 6c and the rotor outer face 4a than two faces having different radii, sealing only in a tangent line.25 The following description is equally relevant for all the embodiments of the invention.As the vane 5, 5’ and the rotor body 4 are the only moving parts in the working chamber W, this means there is no need for contact between any moving parts of the working chamber W. Consequently, there is no need for lubricant here either and contamination of the working fluid can be avoided.30 All relative motion between parts in the working chamber W is controlled by the main shaft 3 and vane moving system 8, 8’. All necessary bearing functions are handled 3493789by the main rotor bearing 13, crank bearing 14, vane shaft bearing 16 and connecting rod bearing 15 (for the embodiment shown in figure 1-4) or vane tip bearing 17 (for the embodiment shown in figures 5-7). All these bearings can then be located away from the working chamber W. Since the motions of the rotor body 4 and the vane 5 5 are motions that may be transferred by the cylindrical shafts 3, 7, 6’, 10, 12. The bearings 13, 14, 15, 16, 17 may be oil lubricated and separated from the working chamber W by simple shaft seals. This is per se known.The functioning of the vane moving system 8, 8’ is thus so that it is linking the connection between the rotor body 4 and the vane tip 6, 6’ without the need of 10 connection inside the working chamber W. The connecting rod 9 is given an oscillating movement by the crank 10.For the embodiment shown in figure 1-4 this provides an oscillating movement of the pivot arm 11 that is linked to the connecting rod 9. Since the pivot arm 11 is fixedly attached to the vane 5, the vane 5 will move accordingly.15 For the embodiment shown in figure 5-7 the vane tip 6’ is fixed to the connecting rod 9 and will move with it. The vane tip 6’ element is rotatably connected to the vane 5, so that the oscillating motion of the connecting rod 9 and the vane tip 6’ also provides an oscillating movement of the vane 5’. In figure 7 it is indicated a through hole, formed as a slot 26 in the static casing wall 2. The slot 26 defines the path where the 20 part of the connection rod 9 that is connected to the vane 5, is able to move.In all the embodiments, the elements of the vane moving device 8, 8’ is arranged so that the rotor body 4, 4’ and the vane 5, 5’ moves by the vane moving device 8, 8’ and not by any contact between the rotary body 4, 4’ and the vane 5, 5’.The rotary machine 1 may further comprise one or more vane support mechanisms 25 20 located in the interface between casing housing 2 and the vane 5. This is illustrated in detail in figure 8.Figure 8 shows the vane support mechanism 20. The vane 5 may have a sealing protrusion 21 extending from the vane sealing face 5a. The protrusion 21 may for instance be positioned at the mid-point of the sealing face 5a.30 The vane support mechanism 20 comprises a cavity K in the casing 2 in which the protrusion 21 can move freely within the pivot range of the sealing vane 5. The pivot 34937810range is the space within the cavity K between end positions O and N as indicated in the figure 8.The protrusion 21 is adapted to seal against a cavity wall 2b effectively, forming two separate closed volumes A and B, that may be connected to the machines working 5 chamber, and therefore containing the working fluid F.The oscillating motion of the vane 5 causes large dynamic forces Fd on the vane 5 and vane movement system 8. The motion will also cause a compression of volume A and expansion of volume B, or vice versa, depending on the direction of the stroke. This produces a differential pressure between volume A and B, which again10 generates a force Fp on the protrusion 21. This force will counteract the dynamic forces Fd, and therefore greatly offload the vane 5 and vane moving system 8.The vane support mechanism 20 further may comprise one or more fluid supply channels 22 connecting each of the two volumes A, B to a compressor port L or H (fig. 1, 4, 5), for supplying fluid into the volumes A, B. There may further be non-15 return valves 23 in the fluid supply channels 22 to prevent backflow and flow between the volumes A, B. The vane support mechanism 20 may further have fluid return lines 24 connecting each volume to the compressor inlet and/or outlet port, a fixed or adjustable throttling device 25, such as a valve, in the fluid return lines 24, to set the maximum obtainable pressure in each volume.20 Referring to figure 8, when the machine is operating, the vane 5 will oscillate so that the protrusion 21 moves between its upper position O and lower position N. The dynamic force Fd will be at its maximum in the direction away from the rotor body 4 when the protrusion 21 is at its upper position O, and its maximum in the direction towards the rotor body 4 when the protrusion is at its lower position b.25 The vane support mechanism 20 uses the vane’s 5 motion to fill and compress working fluid in the two volumes A, B on each side of the vane seal face protrusion 21.As the protrusion 21 is at its upper position O, the volume A will be fully compressed, while the volume B will be uncompressed or expanded, depending on the settings of 30 the throttling device 25. The pressure difference between the two volumes A, B acts on the protrusion 21, exerting a pressure force Fp on the vane 5 acting towards the 34937811rotor body 4, i.e., opposite of the dynamic force Fd.As the vane 5 with the protrusion 21 moves from its upper position O towards its lower position N, the dynamic force Fd is gradually reduced, before changing direction and reaching its maximum in the direction towards the rotor body 4 when 5 the protrusion 21 reaches its lower position N. At the same time the volume A is expanding, and volume B is compressed.By selecting adequate width of the protrusion 21 and adjusting the max pressure in the two volumes A, B, using e.g. the throttling devices 25, the force Fp from the vane support mechanism 20 can counteract the dynamic forces, and greatly reduce the 10 total forces on the vane 5.This is beneficial because it prevents unwanted clearance between the vane tip seal face 6a and the rotor body outer face 4a, arising from dynamic forces FD forcing the vane 5 away from the rotor body 4 as it moves towards its upper position O. In this part of the motion, the working fluid F in the working chamber W is at or close to its 15 maximum pressure, so it is very important to minimize clearances to avoid volumetric losses.Further the support mechanism 20 reduces forces on the connecting rod bearing 15 and vane tip bearing 17. This results in that smaller, lighter bearings and other moving parts can be used, which again means reduction of e.g., size, complexity, 20 cost, and vibrations to the surroundings.Even though the vane support mechanism 20 is illustrated wit the vane embodiment from figure 1, the vane support mechanism is equally applicable for the vane embodiment illustrated in figure 5.The positive displacement rotary machine 1 may be suitable for different purposes, 25 for instance as a compressor and/or expander for gases of gas/liquid mixtures.When working as a driven machine, e.g. compressor or pump, rotational motion is applied to the main shaft 3 by for example an electric motor, to rotate the rotor 4. When working as a driver, e.g. expander, the pressure in the working chamber W drives the rotor 4, and rotational motion is transferred via the main shaft 3 to a 30 consumer, e.g. an electric generator.Working fluid enters the machine through one of the first or second ports L or H, 34937812depending on whether the rotary machine 1 operates as a compressor or an expander.In a compressor, the working fluid enters the working chamber W through the port L. The rotor body 4 rotates clockwise referring to figure 1. Once the sealing line or 5 portion between the rotor body 4 and the casing 2 has moved past the port L, a closed working chamber W is formed between the rotor body 4, the static casing inner wall 2a and the sealing vane 5. The volume of this working chamber W will decrease as the rotor body 4 continues its rotation, and the pressure of the working fluid F entrapped in the working chamber W will increase. Once the required10 discharge pressure is reached, the working fluid F will exit through the second port H.A valve arrangement 18 or similar in the high-pressure port H is necessary to control the machines volumetric ratio. When designed as a compressor, this can be standard compressor valves, or other types of reed valves or non-return valves that will open once the pressure in the working chamber W reaches or slightly exceeds the15 pressure downstream the valve 18. These types of valves require no further control mechanisms.When working as an expander, the valves 18 may need to be controlled to open at a given position, e.g. by a mechanical control such as a cam shaft that sets the valve position based on the rotor body 4 position.20 Even though the figures illustrate different embodiments, it is to be noted that the embodiments of the rotor body 4, 4’ may be used in any of the embodiments 1-3 or 5-7.For instance, the rotor body 4’ of figure 5 may be used together with the vane of figure 5’.25 The vane support mechanism may be used in all embodiments of the invention. 34937813Figure list1 – rotary machine, first embodiment2 - static casing5 2a - casing inner wall2b – casing cavity seal face3 - main shaft4 - rotor body, first embodiment4’ – rotor body, second embodiment10 4a – rotor seal face4b – rotor body – vane seal face4c – rotor body - casing seal face5, 5’ - sealing vane5a – vane - casing seal face15 5b – vane – vane tip seal face6 – vane tip, first embodiment6’ – vane tip, second embodiment6a - vane tip - rotor seal face6b – vane tip - vane seal face20 6c – vane tip – rotor seal face, fixed vane tip 7 - vane shaft8 – vane moving system, first embodiment 8’ – vane moving system, second embodiment 9, 9’ - connecting rod25 10 - crank11 - pivot arm 3493781412 - cross pin13 – main rotor bearing14 – crank bearing15 – connecting rod bearing5 16 – vane shaft bearing17 – vane tip bearing18 - valve20 – vane support mechanism21 – sealing protrusion10 22 - fluid supply channels23 – Flow restrictor, non-return valves24 - fluid return line25 - throttling device26 – slot15 50 – rotary machine, second embodiment60 – rotary machine, third embodimentK – vane support mechanism chamberA – first closed volumeB – second closed volume20 O – vane protrusion upper positionN - vane protrusion lower positionS – sealing lineM – rotational center axis of main shaft and geometrical centre axis of casing bore R – geometrical center of rotor body and crank25 C - center axis of cross pin and vane tipV – center axis of vane shaft 34937815W – working ChamberF – working fluidL - first port - Inlet fluid port /outlet fluid portH - second port -- outlet fluid port/inlet fluid port5 P – length of connecting rodFd – dynamic forces on vaneFp – force on vane arising from differential pressure on sealing protrusion 21 d – diameter of rotor bodye - rotor offset distance10 c – casing inner bore radiusr – rotor seal face radiusv - vane tip radiusf - offset distance between center axis of vane shaft and casing inner bore radius.
Claims
34937816Claims5 1. A rotary machine for fluid processing, comprising a static casing (2) with a first port (L) and a second port (H) for allowing fluid out of and into the rotary machine; the rotary machine comprising a rotor body (4), said rotor body having a rotor body outer face, said rotor body (4) being attached to a main shaft (3), said main shaft (3) being arranged within said static casing (2); said10 main shaft (3) having a rotational centre axis (M) which is coincident with a centre axis of a casing bore (1a) in said static casing (2); said rotor body (4) having a first geometric center (R) arranged an offset distance (e) from said rotational center axis (M) of said main shaft (3); the rotary machine further comprising a sealing vane (5, 5’) having a vane tip (6, 6’); and a vane moving15 system (8, 8’) operationally connected between said rotor body (4) and said sealing vane (5, 5’) for maintaining a vane tip seal face (6a, 6c) of said vane tip (6, 6‘) in a sealing relationship with said rotor body (4); said vane moving system (8, 8’) comprising at least one connecting rod (9, 9’) operationally connected at a first end to said rotor body (4); said at least one connecting rod20 (9, 9’) being connected to a crank portion (10) on said main shaft (3),characterized in that said vane tip (6, 6’) seal face (6a, 6c) having a semicircular cylindrical seal face (6a, 6c), facing said rotor body (4) outer surface;- in a first alternative, said rotor body (4) having a cross section with two different circular cylinder segments, a first segment with an25 outer surface (4b) having a geometric center coinciding with said first geometric centre (R), and a second segment with an outer surface (4c) having a second geometric centre coinciding with said rotational centre axis (M), and said second segment outer surface (4c) being concentric to and co-radial with said casing bore (1a) to30 seal against a casing inner wall (2a) of said bore (1a) at all rotational positions of said rotor body (4); said crank portion (10) being concentric with said first segment outer surface (4b) of said rotor body; said vane tip (6) seal face having a radius (v); said connecting rod (9) at a second end thereof being operationally35 connected to a pivot arm (11) at a cross pin (12) thereof; said pivot arm (11) being rigidly connected to said vane (5); said cross pin (12) being concentric with said semi-circular face (6a) of said vane tip34937817(6), and a length (p) of said connecting rod (9) between the center axes of said crank portion (10) and said cross pin (12) being equal to a radius (r) of said first segment outer surface (4b) plus the radius of the vane tip (v); or5 - in a second alternative, said vane tip (6’) comprising a vane tip element that is rotatable relative to said vane (5’), said vane tip element having a first semi-circular cylindrical face (6b) that is concentric with an axis of rotation between said vane tip (6’) element and said vane (5’), said vane tip element being fixedly connected to said connecting rod (9’), said vane10 tip element having a second semi-circular cylindrical seal face (6c) that is concentric and co-radial with the rotor body outer face (4).2. The rotary machine according to claim 1, wherein the rotary machine further comprises a vane support mechanism (20) located in the interface between said casing (2) and said vane (5, 5’).15 3. The rotary machine according to claim 2, wherein said vane support mechanism (20) comprises a cavity (K) defined in said casing (2), said cavity (K) being open towards said vane (5, 5’), said cavity (K) and a vane seal face (5a) forming a closed chamber; said vane (5, 5’) having a protrusion (21) extending into said cavity (K) and forming a seal towards an inner wall (2b) of20 said cavity (K), thereby dividing said closed chamber into a first closed volume (A) and a second closed volume (B).4. The rotary machine according to claim 2 or 3, wherein said vane support mechanism (20) further comprises a fluid adjusting arrangement (22, 23, 24, 25) providing adjustment of a pressure of said first and/or second volume (A,25 B) to control the movement of the vane (5, 5’).34937818Patentkrav1. En rotasjonsmaskin for fluidprosessering, omfattende et statisk hus (2) med en første port (L) og en andre port (L) for å slippe fluid inn i eller ut av 5 rotasjonsmaskinen; der rotasjonsmaskinen omfatter et rotorlegeme (4), som har en ytre overflate, der rotorlegemet (4) er festet til en hovedaksling (3) som er anordnet inne i det statiske huset (2); idet hovedakslingen (3) har et rotasjonssenter (M) som sammenfaller med en senterakse for en husboring (1a), idet rotorlegemet (4) har et første geometrisk senter (R) som er anordnet 10 en offsetavstand (e) fra rotasjonssenteraksen (M) for hovedakslingen (3); idet rotasjonsmaskinen videre omfatter en tettende vinge (5, 5’) som har en vingetupp (6, 6’), og et vingebevegelsessystem (8, 8’) som er operasjonelt forbundet mellom rotorlegemet (4) og den tettende vingen (5, 5’) for å opprettholde en vingetupptetningsflate (6a, 6c) for vingetuppen (6, 6’) i tettende 15 nærhet til rotorlegemet (4); der vingebevegelsessystemet (8, 8’) omfatter lins en forbindelsesstav (9, 9’) som er operasjonelt forbundet ved en første ende til rotorlegemet (4); idet den minst ene forbindelsesstaven (9, 9’) er forbundet med en veivdel (10) på hovedakslingen (3), karakterisert ved at vingetuppens (6, 6’) tetningsflate (6a, 6c) har en semisirkulær-sylindrisk tetningsflate (6a, 6c), som 20 vender mot rotorlegemets (4) ytre overflate; der- i et første alternativ, rotorlegemet (4) har et tverrsnitt med to ulike sirkulærsylindriske segmenter, et første segment med en ytre overflate (4b) som har et geometrisk senter som sammenfaller med det første geometriske senteret (R), og et andre segment 25 med en ytre overflate (4c) som har et andre geometrisk senter som sammenfaller med rotasjonssenteraksen (M), og at det andre segmentets ytre overflate (4c) er konsentrisk med og koradielt med husboringen (1a) for å tette mot en indre vegg (2a) i boringen (1a) i alle rotasjonsposisjoner av rotorlegemet (4); at veivdelen 30 (10) er konsentrisk med rotorlegemets første segments ytre overflate (4b); at vingetuppens (6) tetningsflate har en radius (v); at forbindelsesstaven (9) ved en andre ende er operativt forbundet34937819med en svingarm (11) ved en krysstapp (12); at svingarmen (11) er fast forbundet med vingen (5); at krysstappen (12) er konsentrisk med den semisirkulære flate (6a) til vingetuppen (6), og at en lengde (p) av forbindelsesstaven (9) mellom senteraksen 5 til veivdelen (10) og krysstappen (12) er like en radius (r) av det første segmentets ytre overflate (4b) pluss radiusen til vingetuppen (v), eller- in et andre alternativ, vingetuppen (6’) omfatter et vingetuppelement som er roterbart i forhold til vingen (5’), at 10 vingetuppelementet har en første semisirkulære sylinderflate (6b) som er konsentrisk med en rotasjonsakse mellom vingetuppelementet og vingen (5’), at vingetuppelementet er fast forbundet med forbindelsesstaven (9’), og at vingetuppelementet har en andre semisirkulær tetningsflate (6c) som er konsentrisk og 15 koradiell med rotorlegemets ytre overflate (4).2. Rotasjonsmaskinen ifølge krav 1, karakterisert ved at rotasjonsmaskinen videre omfatter en vingestøttemekanisme (20) som er anordnet mellom huset (2) og den tettende vingen (5, 5’).3. Rotasjonsmaskinen ifølge krav 2, der vingestøttemekanismen (20) 20 omfatter en kavitet (K) i huset (2) som er åpen mot vingen (5, 5’) slik at kaviteten (K) og en vingetetningsflate (5a) danner et lukket kammer, idet vingen (5, 5’) har et fremspring (21) som strekker seg inn i kaviteten (K) og danner en tetning mot kavitetens (K) indre vegg (2b), og deler det lukkede kammeret inn i et første lukket volum (A) og et andre lukket volum (B).25 4. Rotasjonsmaskinen ifølge krav2 eller 3, karakterisert ved at vingestøttemekanismen (20) videre omfatter et fluidjusteringsarrangement (22, 23, 24, 25) for å justere trykket i det første og/eller det andre volumet (A, B) for å kontrollere bevegelsen til vingen (5, 5’).
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Patent classes

IPC classesF01C 21/08F01C 1/46F04C 2/46F01C 1/39F01C 1/352CPC classesF01C 21/089F01C 1/46F04C 2/46F01C 1/39F01C 21/0809F01C 21/0818F01C 21/0827F01C 21/0836F01C 1/352

Citations

GB 273439 A (A)US 3081707 A (A)US 922189 A (A)US 2005000214 A1 (A1)NO 744622 L (L)GB 600383 A (A)CH 504612 A (A)

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ETNIR AS
ETNIR AS

Org. number: 937766564

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c/o Nikolai Slettebø Toppåsveien 28B 1352 KOLSÅS NO (BÆRUM Municipality, Akershus county)Org. number: 937766564Inventors
Nikolai Slettebø
Toppåsveien 28 B 1352 KOLSÅS NO (BÆRUM Municipality, Akershus county)

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BRYN AARFLOT AS
BRYN AARFLOT AS

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Stortingsgata 8 0161 OSLO NO (OSLO Municipality, Oslo county)
Org. number: 979993269
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