瑞典专利SE1100018A1 Compressor with low friction seal

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权利要求

类似技术

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法律状态

优先权

专利摘要:

公开号:SE1100018A1
申请号:SE1100018
申请日:2011-01-10
公开日:2012-07-11
发明作者:Niels Lennart Ohlsen
申请人:Manomeka Ab；
IPC主号:

专利说明:

the spherical inner wall of the ball 18, 19, duplicate as liquid and / or lubricant seals. In the latter case, the sliders essentially do not put pressure on the surface against which they seal, at the same time as they provide sufficient sealing and enable movement of parts.
The invention further relates to such a compressor with remedies 7, 18, 19 for arranging the ring element with its normal at an angle to the axis of rotation arranged so that the angle is variable, and whereby the compression ratio is changed.
Brief description of the drawings Fig. 1 shows, straight from the side, inner parts of the compressor at a first angle of rotation Fig. 2 shows, from an angle slightly across from the side, inner parts of the compressor at the first angle of rotation Fig. 3 shows, straight from the side , inner parts of the compressor at a second angle of rotation Fig. 4 shows, from an angle slightly across from the side, inner parts of the compressor at the second angle of rotation F ig. Fig. 6 shows, straight from the side, inner parts of the compressor at a third angle of rotation. Fig. 6 shows, from an angle slightly across from the side, inner parts of the compressor at third angle of rotation Figs. Fig. 7 shows a pin drive ring. Fig. 8 shows a wing drive ball Figs. Fig. 9 shows the inner parts with a ring element seen straight from the side and also shows an expression of the ring drive ball. Fig. 10 shows the inner parts with the ring element seen from an angle slightly from the side. Fig. 11 shows an expression of inner parts with partitions and without the ring element Fig. 12 shows inner parts with partitions and the ring element Fig. 13 shows the compressor housing Fig. 14 shows the compressor housing and internal parts in cross section Figs. Fig. 16 shows the ring member with a first body of the sealing vanes. Fig. 16 shows the ring member with a second body of the sealing vanes, ring drive ball and pin drive ball. Fig. 17 shows a detailed view of the central part of the compressor, including sealing pins, ring drive ball and pin drive ball. embodiment of the sealing vanes Fig. 19 shows a further alternative embodiment of the sealing vanes Description of desired embodiments Figures 1-6 show the inner parts of compressor according to the invention in three rotated steps, separated by an angle of rotation of 30 °. The figures are intended to explain the functional basis of the compressor, and the outer casing and other details have been eliminated from the figures for simplification.
The six figures are divided into two groups that illustrate inner parts of the compressor from the side and from an angle just above the plane of symmetry of the inner parts. These two groups consist of Figures 1, 3 and 5 and 2, 4 and 6, respectively. In each of two consecutive figures, it is held the angle of rotation, and the elements are shown from two different angles of view.
For circularly symmetrical elements, the angle of rotation is difficult to determine visually, so rotation angle indicators 1 have been added to the figures. These obviously do not represent physical elements.
Fig. 1 shows, straight from the side, the inner parts of the compressor at a first angle of rotation. Each part shown in the figure rotates as the shaft 6 rotates, which is indicated by the arrow at the bottom of the figure. 4a-b, Sa-b rotate about the axis 6, while the axis 7 rotates, at an angle which may differ from zero, relative to the axis 6. The axis 7 is in all figures 1-6 set at a fixed angle relative to shaft 6. The shaft 7 can be set at a different angle, which gives a different degree of compression than that made in Figures 1-6.
The shaft 6 extends upwards to the wing drive ball 8. which is only partially visible in the center of the illustrated objects. The wing drive ball 8 is, in the embodiment shown in Figures 9 to 12, directly or indirectly mechanically connected to all other parts shown in the respective figures and drives the ring ball, not shown, via pins, or can, in an embodiment shown in Figures 1 to 12, 6 and 16. 17, themselves being directly or indirectly driven by the pin drive ball, in which case the wing drive ball is advantageously integrated with the boundary blades which will be described shortly and which the shaft 6 rotates, the other parts rotate therewith.
In the nearby embodiment, the compressor consists of at least four delimiting wings 4a-b, Sa-b, where the upper Sa and lower 5b delimiting wings consist of thin truncated, cone-shaped elements facing each other with respective tips pointing towards each other. The truncated cone-shaped upper and lower boundary wings are arranged with their central axes coinciding with the central axis of the shaft 6. Said boundary wings can, as previously mentioned, be advantageously integrated in a second embodiment and connected directly to the shaft 6, whereby the wing guide ball can be substantially eliminated. and a homokinetic joint (for example, a Rzeppa joint) can be used to transmit torque between the pin drive ball 20 and the ring drive ball 19, as shown in Figures 16 and 17.
The upper and lower boundary wings define a volume extending between them, which in turn is divided into, in this embodiment, four different volumes with four transverse boundary wings 4a- b. The transverse boundary wings are mainly flat, truncated circular sectors. The transverse boundary wings are arranged between the upper and lower boundary wings and each transverse boundary wing extends from the upper to lower boundary wing and forms a right angle at each intersection between the transverse boundary wing and the upper and lower boundary wings. The transverse boundary wings are evenly distributed around the upper and lower boundary wings, and are, in the presented embodiment, positioned substantially ninety degrees apart. The transverse delimiter wings are present in the present embodiment airtightly connected to the upper and lower delimiter wings, in connection with the compressor housing forming, in this embodiment, four airtight compartments.
Each of four compartments delimited by the six delimiting wings is further divided into a total of eight compartments by a ring element 2, which in turn consists of a number of components, as described below.
The ring element 2 is further substantially shaped as a circular disc, with four slots receiving each of the four transverse boundary wings. To achieve air tightness, the ring element is provided with sealing vanes 3 arranged in the immediate vicinity of each transverse boundary vane, and these will be discussed in more detail below.
The ring element has its center on the rotating axis of the boundary vanes, but is arranged with its axis offset from this axis. This means that as the internal parts of the compressor rotate, the volume of each of the eight compartments increases, decreases or decreases (in cases where the offset differs from zero). This means that liquid entering one of the eight compartments at an angle of rotation, determined by the non-illustrated housing described below, remains in the compartment which the compressor rotates. the volume of the compartment then decreases or increases as the compressor rotates, leading to compression or decompression of liquid, as determined by the ring member. The liquid then leaves the compressor through an outlet in the housing, giving the intended compression or decompression.
Fig. 2 shows, from an angle slightly across from the side, the inner parts of the compressor at the first angle of rotation. In this view, axis 7 is clearly visible.
The angle between the shafts 6 and 7 determines the relative angle between the rotating axis of the ring element and the delimiter wings, and thus the compression ratio is determined.
From this view, an embodiment of the ring drive ball 19, attached to the shaft 7 and arranged inside the wing drive ball 8, integrated in this body with and substantially replaced by the delimiting wings, is also visible.
At the selected angle between the shafts 6 and 7, the ring element reaches all the way from the lower boundary ring 5b to the upper boundary ring 5a causing the compression to reach its maximum.
Figs. 3-6 show, straight from the side and from an angle slightly over from the side, respectively, how the inner parts of the compressor ﬂ surface to a second and then a third angle of rotation. During this rotation, each sealing vane 3 will be moved up or down the transverse boundary vanes and in order to achieve sealing, corresponding elements in the prior art are usually pressed against the transverse boundary vanes by means of springs or some resistant substance. This causes wear on seals and friction in the compressor.
In the compressor according to the invention, however, the sealing vanes 3, 23, 24 are arranged against the transverse boundary vanes without applying any force between the sealing vanes and the transverse boundary vanes, by means of an innovative solution described in detail below.
Fig. 7 shows a tap drive ball and figure. 8 shows a wing drive ball, which has certain common features.
Both are hollow spheres, with a piercing extending through the center of each ball.
The through holders define a central axis for each ball, and two pairs of slots extend parallel to the central axis of both balls. In the presented embodiment, the first method consisting of four wider pin slots 10a-b is placed at a mutual distance of ninety degrees between successive slots around the balls and is intended to have four pin holders for the ring element with which the ring element in this second body is driven. the group of four pairs of narrower drive slots llal-2, llbl-2 are in the presented embodiment also placed at a distance of ninety degrees between the successive pairs, but the second way of slots is provided with essentially 45 degrees relative to the first method, even distances between each slot or pair of slots. The second way of pairing slits is in the present embodiment arranged to receive eight retaining pins for the sealing wings.
The pin drive ball is intended to drive and control the movements of the sealing holder pins 16, and is, as is the case for the wing drive ball, connected to the shaft 6.
In this embodiment, the selector ball 18, to which the shaft 7 is fixedly connected, will lie in between the wing drive ball 8 and the pin drive ball 9, and will be driven by the wing drive ball via pins.
F ig. 8 shows the wing drive ball 8 with the pin drive ball 9, and the shaft 6 connected to both. As can be seen, the wing drive ball and the pin drive ball are arranged so that the corresponding slots in the respective balls overlap each other. This makes it possible to place the seal holder pins in slots and these can spread to the pin drive ball. As corresponding slots overlap, this allows the holding pins to surface up or down in the slots, which makes it possible to angle the ring drive shaft 7 relative to the shaft 6. which enables different degrees of compression.
The driving slots llal-2, llbl-2 allow the sealing vanes to move up and down with the ring elements and control the relative angle of rotation between the sealing vanes and the transverse boundary vanes and transmit the necessary force to drive the sealing holder pins, overcome (lubricated) sealing and friction tapdrivkulan. The sealing holder pins are intended to hold the sealing vanes in the immediate vicinity of, or against the transverse boundary vanes, without applying any force between them. This is achieved regardless of how the ring drive ball is angled relative to the wing drive ball, and through a full revolution of the compressor. In addition, the pins effectively cancel the centripetal force acting on each pair of sealing wings, thereby avoiding friction between the sealing wings and the outer casing. Fig. 9 shows the inner parts with the ring element seen straight from the side, and fig. 10 shows the inner parts with the ring element seen from an angle slightly across from the side. 1 ﬁ g. In particular, it is clearly illustrated how, in this embodiment, the ring elements are provided with holding pins 12a-b extending from the rings to the slots in the ring element.
As shown in figure. 1 through 6 and Figures 16 and 17, the ring elements, in another embodiment, can be easily integrated and connected directly to the shaft 6, in which the embodied wing driver ball can be substantially eliminated and a homokinetic joint (e.g. Rzeppa) can be used to transmit torque between the pin drive ball and the ring drive ball 19, which is apparent from the gurus 16 and 17, in which case the ring element slots 10a-b become superfluous.
The figure also illustrates how the sealing wings 3a1-2 in an embodiment of the invention are arranged in slots in the ring elements, which extend parallel to the upper surface of the ring element. These slots in the ring elements cause the sealing vanes to follow the upward and downward movement along the transverse boundary vanes. This is clearly illustrated in the figure. How slots in the wing driver ball allow upward and downward movement of the sealing vanes so that they are always adapted to the sides of the transverse boundary vanes, to achieve a tight seal.
Fig. 11 shows the inner parts with delimiting wings and with the ring element removed for the sake of clarity. The boundary vanes are in this embodiment, airtightly attached to a wing driver ball, with each transverse boundary vane arranged along the string of the driver ball extending between each slot in the pair of sealing slots.
F ig. 12 shows the inner parts with delimiting wings and the ring element. Again, it is illustrated how the ring member and boundary vanes, in conjunction with the vane drive ball and the non-illustrated outer casing, define eight compartments that increase or decrease in volume as the compressor rotates.
The figure also shows how the slots in the ring element, receiving the sealing vanes, are deep enough to receive substantially the entire width of the sealing vanes, but the drive slots position the sealing vanes so that they extend from the slots, achieving an airtight seal.
Fig. 13 shows the compressor housing 13, which surrounds the inner parts of the compressor and achieves (in the indicated embodiment) eight limited, completely closed, compartments which perform the actual pumping or compression process. The enclosure is provided with inlet openings 14 and openings out 15, through which liquid penetrates into and out of the compressor.
Fig. 14 shows the compressor housing and internal parts in cross-section, and here parts of the details around the seal holder stages are illustrated, which will be discussed in more detail below.
Fig. 15 shows the ring elements with an embodiment of the sealing wings 3al-2, 3b1-2 with attached taps sealing holder pins 16bdl-2, 16acl-2. Each sealing vane is connected to a corresponding sealing vane on the opposite side of the compressor, so that the sealing vane 3a1 is connected to the sealing vane 3cl with the sealing holder pin 16acl, and correspondingly for each pair of oppositely placed sealing vanes.
For each pair of sealing vanes, such as the pair 3a1-2, the respective seal holder pin 16ac 1-2 runs parallel to the seal holder pin on the seal vane pair 3cl-2 on the opposite side of the center. This would have meant that a parallel pair of seal holder pins would cross another pair of seal holder pins in the center, but the seal holder pins are bent near the center and thereby bent up and down, respectively, in the figure. This bending near the center eliminates intersection problems that would otherwise have occurred.
F ig. 16 shows a second embodiment of the ring elements, the sealing wings. ring drive ball 19 and pin drive ball 20.
In the foregoing embodiment, the sealing vanes were shaded for easy identification, while Figures 16-17 show objects other than the sealing vanes which dashed. The second embodiment differs from the first embodiment in that eight sliders 17a1-2, 17b1-2, 17cl-2, 17dl-2 control the sealing holder stages via guides 22a-di the ring drive ball 19 and in that the ring drive ball is integrated with the ring elements 21 integrated and directly connected to the shaft 6, In practice eliminating the wing drive ball. A homokinetic joint (for example an Rzeppa joint) can be used to transmit torque between the pin drive ball 20 and the ring drive ball, the Rzeppa style balls placed in the grooves 21.
Fig. 17 shows a detailed view of an embodiment of the central part of the compressor.
Near the intersection between the sealing wings and the sealing holder pins, sliders l7a1-2, 17b1-2, 17c1-2, 17d1-2 are illustrated in more detail. Said controls may be limited by guides 22a-d in the ring drive ball 19, which ensures that the seal holder pins and thus the sealing wings are kept substantially in the plane of the ring element, 2, substantially making the relative local movement between the sealing wings and the ring element wings 2a-d frictionless. Said controls can, if equipped with substantially spherical surfaces facing the spherical inner wall of the vane drive ball, double as lubricant and / or liquid seals in which case the controls, as they rotate around the center of the compressor, move along the inner wall of the annular ball and adjust accordingly. regardless of the position of the sealing vanes in relation to the transverse boundary vanes. Again, this means that essentially no force is applied to the controls against the inner wall of the ring drive ball, reducing wear and friction. If sufficient adjustment is made, lubricant and / or liquid tightness can be achieved. In applications with sufficiently small loads on the seal holder pins, it becomes possible to use the described parts of the compressor completely without liquid lubrication and all necessary lubrication can be obtained via solid lubricant, such as for example PTFE.
Fig. 18 shows an alternative embodiment of the sealing wings where the sealing wings sweep around the ring element instead of penetrating into the ring element through slots.
Fig. 19 shows a further alternative embodiment of the sealing wings where the sealing wings sweep around the ring element to a lesser extent than in Fig. 18, again instead of penetrating into the ring element through slots. In the description above, the word "compressor" is used as a general term and by "compressor" is meant a compressor, a pump used to increase pressure, a pump used to reduce pressure or other similar machine.

权利要求:
Claims (5)
[1]
1. l)
[2]
2.)
[3]
3.)
[4]
4.)
[5]
5.) A compressor consists of a rotatable part enclosed in a housing (13) with liquid in- (14) and outlets (15), where a part is rotatable about a first axis of rotation, and where said part consists of at least one transverse wing (4a-b), the enclosed volume again divided by a rotatable ring element (2) which can be in principle flat and which is rotatable about a second axis of rotation and which extends between adjacent transverse wings and which is provided with means (7, 18 , 19) for arranging the ring element with its normal at an angle to the first axis of rotation, and where further the ring element is provided with slots for receiving at least one transverse wing, characterized in that in one embodiment of the invention the ring element is provided with other slots for receiving against sealing wings (3, 3al-2, 3bl-2, 3c 1-2, 3dl-2), while the sealing wings in other embodiments (23, 24) of the invention at least partially wrap around the ring element; in each embodiment of the invention the sealing vanes extend substantially parallel to the ring member and the sealing vanes are attached to sealing holder pins (16bdl-2, 16acl-2) which extend substantially towards the center of the compressor and pass through drive slots (1lal-2, 11b ) in at least one ball element (8, 9, 20) arranged around the center of the compressor, the driving slots extending substantially parallel to the axis of rotation of said ball elements and thus substantially parallel to the transverse wings. A compressor according to claim 1, characterized in that the sealing vanes are arranged in pairs with each pair of sealing vanes lying on substantially opposite sides of the second axis of rotation, and where such a pair of sealing vanes are connected to a sealing holder stage. A compressor according to claim 2, characterized in that at least one sealing holder stage is provided with a central part offset substantially in the direction of the second axis of rotation. A compressor according to any one of the preceding claims, characterized in that at least one ball element (18, 19) is provided with a substantially spherical inner wall, and in that the sealing holder pins are provided with guided sliders (17, 17al-2, 17bl-2, l7c l-2. l7d1-2), and where guides (22a-d) limit the controls and thus the sealing vanes to limited mobility in the plane of the ring element (2), which ensures an almost frictionless local movement of the sealing wings relative to the ring element. A compressor according to any one of the preceding claims, characterized in that the means (7, 18, 19) for arranging the ring element with its normal at an angle to the first axis of rotation are arranged so that the angle can be changed.

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同族专利:

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US9057375B2|2015-06-16|

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引用文献:

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CN101368566A|2008-08-08|2009-02-18|郑良才|Cylindrical compressor or vacuum pump|GB2508426A|2012-12-02|2014-06-04|Jorgen Egil Tveit|Rotary engine|

CN109162762B|2018-09-05|2020-12-25|上海理工大学|Spherical ball expander|

法律状态:

优先权:

申请号 | 申请日 | 专利标题

SE1100018A|SE535608C2|2011-01-10|2011-01-10|Compressor with low friction seal|SE1100018A| SE535608C2|2011-01-10|2011-01-10|Compressor with low friction seal|

PCT/SE2011/000249| WO2012096597A1|2011-01-10|2011-12-28|Compressor with low friction sealing|

EP11855854.3A| EP2619459A4|2011-01-10|2011-12-28|Compressor with low friction sealing|

JP2013548383A| JP5706542B2|2011-01-10|2011-12-28|Compressor with low friction seal|

US13/885,100| US9057375B2|2011-01-10|2011-12-28|Compressor with low friction sealing|

CN201180029705.0A| CN102959246B|2011-01-10|2011-12-28|There is low friction sealed compressor|

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