JPS6027796A - Scroll type machine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION This issue 8A relates to a fluid transfer device, particularly a scroll-type machine suitable for compressing gaseous fluids and having improved (larger) volume/pressure ratio characteristics. It is something.

Devices for transferring various types of fluids commonly include "scroll" devices ("5cro11" appara
There is a class of machines called tus.

This type of device is a fluid expander,
displacement engine
), pumps, compressors, etc., and the present invention can be used for any of these machines. However, for illustrative purposes, the embodiments described below relate to compressors for gaseous fluids.

Scroll devices generally include two helical scroll wings of similar shape each supported to form a scroll member on separate end plates.
ap) f, equipped. The two scroll members are
One scroll wing is 180° from the other scroll wing
They are fitted into each other so as to be rotationally displaced. This device consists of one scroll member (orbital scroll member)
bitingscroll) f The other scroll member (fixed scroll - f i Xedscroll)
flank of each wing relative to
It operates by pivoting so that a moving line contact is made between them to form a moving isolated crescent-shaped fluid-receiving pocket.

A spiral is generally an expansion line of a circle.
a circle (4), which ensures that during operation there is no relative rotation between the scroll members, i.e. the motion is a pure curvilinear translation (curvilinear translation).
Ideally, the line should not rotate. The fluid receiving pocket conveys the fluid to be treated from a first region of the scroll device where a fluid inlet is provided to a second region of the scroll device where a fluid outlet is provided. The volume of the sealed fluid-receiving pocket changes as the pocket moves from the first region to the second region. At any given moment there is at least one pair of sealed fluid-receiving pockets, and when there are multiple pairs of fluid-receiving pockets at the same time, six pairs have different volumes.

In a compressor, a second region is at a higher pressure than a first region and is physically located in the center of the device, and the first region is located at the outer periphery of the device.

Generally speaking, the greater the helical span of the scroll blade, the greater the total possible reduction in the volume of the fluid-receiving pocket (i.e., the possible volume ratio) as the pocket moves into the second region. (larger), ma7' (the larger the volume ratio, the larger the pressure ratio of the machine.

The fluid receiving pocket formed between the scroll members is 2
One of them is the tangential contact along the axial direction between the wing helical surfaces caused by the radial force (side sealing - flank).
sealing ), the other one has six flat edge surfaces (
14 (tip sealing) and the opposite end plate caused by an axial force (tip sealing).

In order to obtain high efficiency, the contact between both types should be good)
requires no relative rotation between the scrolls to obtain a good seal.

The concept of scroll-type devices has been known for some time and it has been recognized that they have unique advantages. For example, scroll machines have high isentropic and volumetric efficiency, which makes them relatively compact and lightweight for a given capacity. The machine also operates quieter and with less vibration than many other compressors because it does not use large reciprocating parts (e.g. pistons, connecting rods, etc.), and all fluid flow is controlled by multiple compressors. Since simultaneous compression in opposing pockets is performed in one direction, τ
Less vibrations caused by pressure. The machine also has unique tolerance to fluid contamination, as it utilizes a relatively small number of moving parts, has a relatively low velocity of motion between the scrolls, and is less susceptible to fluid contamination. For this reason, it is easy to provide high reliability and long life.

One of the most difficult problems in designing scroll machines concerns the techniques utilized to prevent relative angular movement between the scrolls as they pivot relative to each other. One of the most common approaches to this problem is to use an Oldham coupling (slider coupling) that operates between the fixed part of the orbiting scroll device.

Oldham joints typically include an Oldham ring and two sets of lug or slider blocks.

Does the Oldham ring have a groove on one side of it? has been formed,
The groove runs in a direction perpendicular to a similar groove formed on the other side of the ring. - sets of key members are connected to the surface of the orbiting scroll and are connected to the one 11111 in the Oldham ring;
Another set of key members are fixed to the fixed scroll reed or machine housing and are disposed in grooves on the other side of the Oldham ring. The Oldham joint reciprocates parallel to the groove containing the Oldham ring, the fixed scroll, or the other set of key members fixed to the housing. Therefore, the angular movement ( rotational displacement)
Control everything you do, that is, prevent it.

US Pat. No. 1,4,121,488 discloses a machine of the above rA construction.

Other known devices for controlling the relative rotation between scrolls include the first patent (Japanese Patent Application No. 58-2436
7), which utilizes a multiple drive system in which both scrolls are rotated around different centers. However, the rotational control means do not form part of this invention, and in the following illustrative description, an Oldham coupling or similar device which imparts pure curvilinear translation between both scrolls will be used. , it is assumed that the rotation is controlled. For simplicity, it is assumed that the shape of the scroll blade is a circular expansion and expansion line.

For a given blade length and number of blades, the present invention provides a
A novel scroll-type machine with a unique scroll member capable of providing pressure ratios is provided. The same scroll-type machine therefore has a much reduced diametrical dimension than its predecessor for a given volume/pressure ratio (this ratio is usually the starting point for the design of a scroll-type machine). . Furthermore, since the required blade span for a given volume/pressure ratio is reduced, the compressor can be provided with a larger discharge hole. A very simple structure in which the shape of the blade tip and end plate is changed so that when the pocket is pressed, the volume of the pocket is reduced not only in the radial direction, as in the conventional case, but also in the axial direction. So, I'll make you gain.

Hereinafter, the present invention will be described in detail with reference to all the drawings.

Since the principles of the present invention are applicable to almost all scroll type machines and scroll type machines are well known, only the scroll member is shown in its entirety in the drawings. The method of forming the scroll member, the method of assembling it into the machine, the method of restraining it from rotating, the method of driving it, etc. may all be in accordance with known principles.

In FIG. 1, an orbiting scroll member 10 and an I fixed scroll member 12 are illustrated. These scroll members 10, 12 are normally intermeshed with each other, but in FIG. 1 they are shown unfolded, much like an open book, so that the details of their shape can be seen.

The orbiting scroll member 1O has a continuous spiral blade 14 which extends spirally outwardly from the central axis of the machine and has an extension of at least 1080 degrees (3 turns of the reed). Open angle or roll angle
e) 'lt, has. medial and lateral degrees) only
Although it is used as a functional part, the three turns are important because the 1/2 turn on the outer end side of the outer wing side surface and the 1/2 turn on the inner end side of the inner wing side surface do not function. ,Needed. The blade 14 has a uniform thickness in the radial direction,
The outer wing side surface and the inner wing side surface, which face each other, are equally spaced apart in the radial direction.

At the outer edge of the wing 14 in the axial direction, an end plate 16' is disposed for closing the Im radiation space between the facing typical surfaces. This end plate 16 includes 18 outer end sealing surfaces for sealing the outer arched portion of 14 at υ;
They are provided on the wing side surfaces tfjJ that face each other. wing 1
The inner end sealing surface 2° (shown with shading) for complete sealing of the inner arcuate portion of 4.

) are also arranged between mutually facing typical surfaces of the wing 14. These end sealing surfaces 18, 20 are flat and perpendicular to the axis of the machine, the outer end sealing surface 18 being arranged axially more outwardly than the inner end sealing surface 20.

The outer end sealing surface 18 and the inner end sealing surface 2° are connected to each other by a cylindrical transition surface 22.
is formed about a center line of curvature parallel to the axis of the machine and has a radius equal to one-half the radial spacing between exemplary surfaces facing each other in the wing 14. This radius is also the turning radius of the machine.

The wing tip sealing surface is disposed on the inner edge of the wing 14 in the axial direction, and is connected to the outer wing tip sealing surface 24 disposed along the outer arched portion of the wing 14 and the inner arch. It has an innermost sealing surface 26 and a gold plate 1 disposed along the shaped portion. These tip sealing surfaces 24,26 are flat and perpendicular to the axis of the machine, with the outer tip sealing surface 24 being arranged axially inwardly than the inner tip sealing surface 26. The outer end sealing surface 24 and the innermost sealing surface 26 are connected to each other by a cylindrical transition surface 28, which is formed around a center line of curvature parallel to the axis of the machine. and has a radius equal to one-half the thickness of the wing 14 in the radial direction.

The center line of curvature of the transition surface 220 and the center line of curvature of the transition surface 28 are arranged at a distance of about 18θ degrees from each other about one axis of the machine, and the heights of both the transition surfaces 22.28 in the axial direction are the same. is equal to

Fixed scroll member 12f'i, orbiting scroll member 1
0 blades 14 and a continuous spiral blade 32 made of mirror-symmetrical gold. At the outer edge position of the blade 32 in the axial direction, an end plate 84t is disposed for closing the open space between the facing typical surfaces. The end plate 34 has an outer end sealing surface 36 between the mutually facing typical surfaces for sealing the outer arcuate portion of the wing 32.

An inward end sealing surface 88 (drawn with shading) for sealing the inward +7 arched portion of the wing 32 is also disposed between the opposing wing sides of the wing 32. has been done. These end seals 36 and 38 are also flat and perpendicular to the axis of the machine, and the outer end seals 36 are arranged axially more outwardly than the inner end seal surfaces 38. The side sealing surface 36 and the inner end sealing surface 88 are connected to each other by a cylindrical transition surface 40 which is parallel to the outer arcuate portion of R32. The tray includes an outer wing tip seal surface 42 disposed along the inner side arched portion and an inner bulletin seal 44 disposed along the inner arched portion. These wing tip sealing surfaces 42, 44 are flat and perpendicular to the machine line 11II, with the outer tip sealing surface 42 being located 11111 further inward in the axial direction than the inner end sealing surface 44. . The outer end sealing surface 42 and the inner tip sealing surface 44 are connected to each other by a cylindrical transition surface 46 formed about a center of curvature parallel to the axis of the machine. and has a radius equal to one-half the thickness of the wing 82 in the radial direction.

Similar to what was described above regarding the orbiting scroll member 10,
The centerline of curvature of transition surface 400 and the centerline of curvature of transition surface 46 are spaced approximately 180 degrees from each other about the axis of the machine.

The end plate 84 also contains fluid compressed by the compressor. A relatively large discharge boat 30 capable of discharging is provided at the center of the 0 end plate 16, which is located at the center to facilitate the discharge of compressed fluid, and has a shape similar to the above-mentioned discharge port 30. A groove 48 is provided which is aligned with the discharge boat 30.

The orbiting scroll member lO performs a circular orbiting motion relative to the fixed scroll member 12, and is supported by a conventional support method (not shown) as shown in FIG. (a) the outer exemplary surface of one of the wings 14, 82 sealingly engages the inner exemplary surface of the other wing; (b) ),
The outer tip sealing surface 24 sealingly engages the outer tip sealing surface 86, (C) the inner tip sealing surface 26 sealingly engages the inner end sealing surface 38, and (d) ), the outer tip seal surface 42 sealingly engages the outer end seal surface 18; (e) the inner tip seal surface 44 sealingly engages the inner end seal surface 20; (f), during a portion of the pivoting motion, the cylindrical transition surface 26 sealingly engages the cylindrical transition surface 40; (S), during a portion of the pivoting motion, the cylindrical transition surface 40; 46 are mated such that they sealingly engage the cylindrical transition surface 22 to form a sealed fluid-receiving pocket that changes in volume due to the relative pivoting movement of both scroll members 10.12. ing.

・ Figure 2 shows the basic shape of a typical scroll according to the present invention. In the figure, 100 is the base circle for generating the expansion line (involute curve) that completely determines the blade shape, and 102 is the true side surface. 104 is the expansion line of the circle 100 that determines the inner surface of the wing. Assuming that the figure depicts an orbiting scroll member, cylindrical transition surfaces 22 and 28 are shown.

In order to obtain uniform field contraction within the pockets of the six pairs of fluid-receiving boxes, the curvature center of the transition direction 22.28 should be located on a parallel straight line that is tangent to the generation base circle 100. be. Therefore, transition plane 220 centerline of curvature 10
5 is located at the negative tangent 106 of the base circle 100, and the center line of curvature 10'7 of the transition surface 28 is located at the other tangent 108 of the base circle 100. tangents 106 and 10
8 must be parallel to each other, but the center of the first transition plane (between the outer and inner end sealing surfaces) is at least 360 degrees from the outer edge of the functional area in the wing. It can be placed at any point in the middle.

The position of the center of the first transition surface as described above is necessary in the inlet section of the working cycle to ensure the inlet of the entire amount of fill fluid. The second transition surface center (between the outer and inner immediate sealing surfaces) is therefore approximately 180 degrees further from the outer functional area edge of the wing. The center line 105 is located midway between typical surfaces facing each other in the wing, and the 0 transition surface has no bending points and its edge is in contact with the y4 side surface where it intersects. are doing. Good sealing and therefore high efficiency'f! : In order to achieve K, it is essential that the scroll members 10, 12 have a shape that is mirror-symmetrical, properly meshes 9, and is 180 degrees out of phase with respect to the axis of the machine. 0 The operation of the scroll type machine according to the present invention is shown in FIGS. 8-9.
This can be understood by referring to FIG. While moving in a clockwise direction of 1 Av in a circular orbit having a diameter equal to the spacing between typical surfaces facing each other in the orbiting scroll member or wing relative to the fixed scroll member, the scrolls mesh as shown. You should see that.

8-9, the swirler 14 is pivoting relative to the fixed wing 82 in a clockwise circular motion. Figure 3 shows the state after the pressure am has completed the first 860 degrees of crank rotation, and the state in which the orbiting scroll has completely rotated by 360 degrees with respect to the frozen fixed scroll.
It shows. During this pivoting movement, the outer wing moves from a closed position (a position similar to that shown in FIG. 8) to a fully open position (a position W similar to that shown in FIG. 4). and then moved back to the blocking position exposure actually illustrated in FIG. 8, for which reference numeral 2 (
) Two complete charges of suction gas, denoted 0 and 202, are fully taken in. At this point all of the inhaled gas is in the "tal" chambers ("tal" chambers),
a chamber formed between the outer end sealing surfaces 18 and 86;
It's inside.

During the next 180 degree rotation, the packings 200, 202 move to the position shown in FIG.
．． Part of 202 is in the long room, and the other part is in the "short" room.
There is a chamber (5 hort'chamfers) in the chamber formed between the inner end seal surfaces 20 and 38. ,
J: The filling portion in the short chamber is shown as having a higher density of shaded points on the drawing than the filling portion in the long chamber. Furthermore, due to the 180 degree crank rotation, the device is
9 taken in the position shown in Figure 5 and further rotated 180 degrees (10 degrees to take the position shown in Figure 6. At this point, all of the filling 200 degrees 202 is in the short chamber, so the same Packing 20 +1. 202I'lt, instead of the customary radially placed and compressed scales, the short chamber has a smaller axial height than the long chamber (otherwise (All are equal.) The fact is that they are also under compression in the axial direction, so that a greater volume reduction is achieved than would be achieved if the chambers all had the same axial height.

The 900 degree position shown in FIG. 6 is the earliest point at which the dispense cycle can begin. However, the illustrated outfit @ has an additional 4
It is assumed that no discharge is performed until the rotation of 5 degrees has been performed and the position shown in FIG. 7 is reached. Discharge is from wing 14
．． Start at 1μ, as shown in FIG. 7, where the inboard tips of 82 are sealingly engaged with each other. As the crank rotates further, 1125 shown in FIG.
The chamber opens into the discharge boat 80 as shown at the position of
Dispensing continues during a further 180 degree rotation of the housing to approximately 1305 degrees as shown in FIG. A bag barrel constructed in accordance with the principles of this invention provides a good seal throughout its complete operating cycle. Adjacent exemplary surfaces of each scroll member customarily sealingly engage each other, similar to the manner in which opposing tip and end sealing surfaces sealingly engage each other, and the respective transition The surfaces fit together in a sealing manner as seen from the drawing. For example, during the first 360 degrees of rotation, only inhalation takes place until complete inhalation blockage occurs. Therefore, during the suction phase of the operating cycle, sealing of the transition surface is not critical for initial volume changes. After that, the fluid filling section starts from 360 degrees and continues up to 900 degrees, from the relatively thick long chamber to the relatively small short chamber, as can be clearly seen from Figures 4, 5 and 6. Compression is performed. Each transition plane is located at the position (8) in Figure 3.
60 degrees) to the position of FIG. 4 (540 degrees). 540 degrees (Figure 4) and 720 degrees (
During the same cycle, leakage across the entire transition area is simply due to two equally sized surfaces being compressed into each other in equal proportions. This is a leak between the fillings. Therefore, although mixing may occur, no efficiency loss occurs. Thereafter, starting from 720 degrees (FIG. 5), the transition surfaces are rotated through the next 180 degrees and are sealingly engaged until the device reaches the 0900 degree position (not shown in FIG. 6). In the case of the glue shown in Fig. 6, both the fillings are entirely in the short chamber as shown in the figure, so the transition surface does not touch the filling at all. Fig. 10 shows the phenomenon that occurs in this device. is shown in a graph. In FIG. 10, the chamber volume is plotted on the vertical axis, and the crank angle is plotted on the horizontal axis.A suction cycle occurs during the first 360 degrees (one revolution) of crank rotation from point 0 to point C. The same inhalation cycle continues until complete inhalation blockade is achieved at point C.

There should be no transition band during the first 860 degrees of the scroll wing feature. Subsequent rotation then causes compression. If the end plate were completely flat and coplanar with the elongated chamber end sealing surface, as shown in FIG. 1θ, the compression line would extend from point C to point ``. On the other hand, if the compressor was originally designed with a flat end plate flush with the short chamber end sealing surface, the compression would be in a straight line from point d to point d. (although the total volume of incoming fluid is only the volume at point CI). If desired, compression may begin at a later point in the operating cycle (e.g., point CI). However, in this example, the compression from the long chamber to the short chamber as described above starts at point C and continues for 11 revolutions at point dt- of 900 degrees. The complete cycle is shown as a straight line in Figure 1O for illustrative purposes, but in the previous machine it would probably have been slightly curved.At point d, complete compression and all of the fluid transferred to the short chamber is reached. Since the blockage has been obtained, it is possible to start dispensing at the point d.On the other hand, in the zero-tree embodiment, where continued compression is also possible if desired, from the point d A 45 degree rotation to point e (945 degree point) provides further radial compression; point e moves to a position where the inner end of the vane releases the sealing engagement and the discharge cycle begins. This is the starting point.The discharge continues for one revolution from the end of compression at point e to point f.

The improvement in the volume ratio and therefore the pressure ratio by the machine according to the invention is very clearly demonstrated from Fig. 1θ, where the conventional machine with the minimum blade length has the same value at point q when the crank rotation angle is the same. Whereas the machine according to the invention has a much smaller final volume, having the value at point d, both machines initially have an equal amount of fluid is introduced into the machine.

It can be changed according to the historical principle. It is also possible to have multiple steps or transition zones to provide a larger or more gradual increase in volume/pressure ratio, as will be readily understood by those skilled in the art.

A machine constructed in accordance with the principles of this invention will have a minimum operating crank angle of 1280 degrees for l-output.

To achieve this, it takes 3 turns (as mentioned above)? It is necessary to have The machine illustrated in the drawings has an additional 45 degrees of compression stroke and therefore a total crank angular displacement of 1305 degrees. The wings have therefore been lengthened by 45 degrees.

In this specification, the "roll angle" between two points (first and second points) on the wing is defined as a tangent to the generation base circle and a straight line passing through the first point and the generation base. It refers to the angle between the other tangent to the circle and a straight line that curves through the second point.

With this 1, regarding the present invention, true linear translational motion (curv
The description has been given illustratively in connection with a scroll-type machine that utilizes an Oldham coupling or similar device to perform near motion, and that has a circular expansion and expansion line. As will be appreciated by those skilled in the art, the present invention may be embodied in other types of scroll-type machines. For example, as described above, the present invention can be embodied as a scroll type machine in which a link mechanism is provided in place of the Oldham joint, etc., and the blade shape of the first scroll blade is modified, and in such a case, The same applies to the rc described above for the first non-embodiment.

The parts that engage each other in the transition region have complementary shapes in all parallel planes perpendicular to the axis of the machine, so that the parts contact and seal each other for 180 degrees of each turn. It has to be something. The portion should also be tangential to the adjacent exemplary surface in all parallel planes such as . Assuming that the scroll orbit is circular and there is no relative rotation between the scroll members, the required shape is the shape of each transition surface (with multiple υ radius ), but the radii do not need to be equal in each parallel plane. For example, the transition plane is shown in Fig. 11, Fig. 12, Fig. 1.
Even if it is a conical surface as in the second embodiment shown in FIG. 3, it is not rounded or chamfered as in the eighth embodiment shown in FIGS.
It may be a substantially cylindrical surface. Other shapes of the transition surface are also possible. If the orbit is not circular or there is limited relative rotation between the scroll members, the shape of the transition surface should be calculated mathematically to achieve contact and sealing for 180 degrees during each revolution. Must be set. The circular shape for a given machine does not, however, need to be of equal volume (equal radius) within each of the parallel surfaces as described above, just as a cylindrical surface could be replaced by a full conical surface.

In the illustrated case, the discharge port 30 is circular, but
The discharge boat can be of any desired shape according to customary standards. Even in the event of collapse, the dimensions of the discharge boat according to the present invention can be made much larger than would be possible with conventional scroll-type machines at a given pressure ratio.

[Brief explanation of the drawing]

'f, Figure 1 shows a pair of scroll members embodying the principles of this invention, which are normally engaged with each other, but are separated in the same way as when opening a book. FIG. FIG. 2 is a schematic diagram showing a geometrically flat curved form of a scroll member according to the present invention. Each figure is a cross-sectional view of a blade in a scroll-type working machine according to the invention, showing a plurality of angular movement positions. FIG. 10 is a graph plotting the volume of a sealed chamber f as a function of crank angle. FIG. 11 is a partial cross-sectional view of a second embodiment of the scroll member, showing a cutting line vc corresponding to the line xx in FIG.
It shows the G-section. FIG. 12 is a partial cross-sectional view of an embodiment of the hill distribution 2, showing a cross section taken along a cutting line corresponding to the y--y line in FIG. Figure 13 (is a partial cross-sectional view of the embodiment of the old distribution 2;
The cross section taken along the cutting line corresponding to line z-z in the figure is omitted. Figure i14 is a partial cross-sectional view of the third embodiment of the scroll capital, and the cross section of the bath 9 is shown on the cutting line corresponding to the x-X line in Figure 1. 3 is a partial cross-sectional view of the embodiment No. 3, in which a cross section along a cutting line corresponding to the y-y line in FIG. 1 is omitted. FIG. 16 is a partial cross-sectional view of an embodiment of the power distribution 3, showing a cross section taken along a cutting line corresponding to the Z-X line in FIG. DESCRIPTION OF SYMBOLS 10... Orbiting scroll member, 12... Fixed scroll member, 14... Wing, 16... End plate, 18...
Outer end sealing surface, 20... Inner end sealing surface, 22...
- Transition surface, 24... Outer different light sealing surface, 26... Inner different light sealing surface, 28... Transition surface, 32... Wing, 3
4... End plate, 36... Outer end sealing surface, 88...
Inner end sealing surface, 4()... Transition surface, 42... Outer different light sealing surface, 44... Inner different light sealing surface, 46 Pa.
Transition surface, 30... Discharge 1" j boat, 48... Concave groove,
100... Expansion line generation base circle, 102... Expansion line, 104... Expansion line, 200.202... Filler (
filling fluid).

Claims (1)

[Claims] 1. A first scroll member and a second scroll member are meshed with each other, and the fluid is moved in a direction parallel to a plane perpendicular to the axis of rotational motion. A scroll-type machine configured to compress
Means for moving the fluid in a direction parallel to said axis to obtain simultaneous additional compression of said fluid? A scroll-type machine characterized by: 2. A scroll-type machine according to claim 1, comprising: A. an end plate; and B. a spiral blade extending outward from a first axis perpendicular to the Jz end plate. A wing to be attached to the end plate, and C1 a flat first surface disposed between the row sides of the first portion facing in the spiral direction of the above wing, as the end plate. D, a flat second face metal disposed between the row sides of the second portion along the spiral direction of the wing;
means for forming the end plate; A scroll-type machine that is configured so that each one is located inside. 8. A scroll-type machine according to claim 2, wherein the blade has a wing side surface in the shape of a circular expansion and expansion line. 4. A scroll type machine according to claim 2, wherein the first surface and the second surface are connected to each other by an intermediate transition surface. 5. The scroll type machine according to claim 4, wherein the transition surface is formed into a surface having a constant radius of curvature in a plane perpendicular to the first axis. scroll type machine. 6.% The scroll-type machine according to claim 5, wherein the transition surface has a second axis parallel to the first axis.
A scroll-type machine that is formed on a cylindrical surface with an axis of . 7. A scroll type machine according to claim 5, wherein the transition surface is formed as a conical surface. 8.% Allowance The scroll type machine according to claim 5, wherein the intersection of the transition surface and the tenth surface or the second surface is formed into a rounded corner. A scroll-type machine. 9. The scroll-type machine according to claim 8, wherein the corner portion is located at the intersection of the transition surface and the outermost portion of the first or second surface. A scroll-type machine is located. 10. The scroll-type machine of claim 5, wherein the second axis extends at least about 860 degrees from the outer end of the blade. 11. The scroll-type machine according to claim 2, wherein the blade has a diameter of at least 90 in the helical direction.
A scroll-type machine with a functional section length spanning a range of 0 degrees. 12. The scroll type machine according to claim 2, wherein the second member is disposed inward of the first surface when viewed in the radial direction. 18. The scroll type machine according to claim 12, wherein the second surface is arranged at a greater distance from the surface of the end plate than the first surface. machine. 14. A scroll type machine according to claim 2, comprising means for forming a discharge port passing through the end plate at its center. 15. The scroll-type machine according to claim 2, comprising means for forming a groove in the center of the end plate. 16. A scroll type machine according to claim 2, wherein the first surface and the second surface are connected to each other by an intermediate concave transition surface. . 17. The scroll type machine according to claim 2, wherein the first surface and the second surface described in 111 are connected to each other by an intermediate conical transition surface. scroll type machine. 18. The scroll-type machine according to claim 17, wherein the central axis of the conical transition surface? 1
1. A scroll-type machine that is parallel to the axis described above. 19. A scroll type machine according to claim 2, wherein the first surface and the second surface are connected to each other by an intermediate cylindrical transition surface, and 611. A scroll type machine, wherein each intersection of the transition surface and the first surface and the second surface has a rounded cross-sectional shape. 2. A scroll type machine according to claim 19, wherein the axis of the cylindrical transition surface is parallel to the first axis. 2. A scroll-type machine according to claim 1, comprising: A. a substantially flat end plate; and B. a spiral extending outward from a first axis perpendicular to the end plate. A wing having a shape of C0, which is attached along one end edge in the axial direction with respect to the end plate; D, means for forming a first wing tip surface spanning a range of D, on the other end edge of the wing in the axial direction;
means for forming the entire second wing tip surface extending over the range of the second portion along the spiral direction of the wing; , J: A scroll-type machine configured to lie in two mutually spaced planes perpendicular to the axis of description 1. 2. A scroll-type machine according to claim 21, wherein the blade has a circular wing side surface in the form of a circular expansion and expansion line. 2. A scroll-type machine according to claim 21, wherein the first blade tip surface and the second blade tip surface marked with I+] are connected to each other by an intermediate transition surface. Scroll m41M. 2. The scroll-type machine according to claim 23, wherein the transition surface has a shape of a metal layer with a constant radius of curvature in a plane perpendicular to the first axis. Nuclor type machine being formed. 2. The scroll type machine according to claim 24, wherein the transition surface is formed as a cylindrical surface having a second axis parallel to the first axis. 2. A scroll type machine according to claim 24, wherein the transition surface is formed into a conical surface. 2. The scroll-type machine according to claim 24, wherein the intersection of the transition surface and the first blade tip surface or the second blade tip surface is formed with a rounded corner. Scroll type machine which is used for forming. 2. The scroll-type machine according to claim 27, wherein the corner portion is connected to the transition surface and the first corner.
The blade tip surface of the scroll-type machine is located at the intersection with the outermost part of the second blade tip surface. 2. The scroll-type machine of claim 21, wherein the second axis extends at least about 360 degrees from the outer end of the blade. i30. 22. A scroll-type machine as claimed in claim 21, in which the blades have a full functional length spanning a range of at least 900 degrees in the helical direction. 31. Claim 21 The nine-scroll type machine is characterized in that the i++ second blade tip surface is disposed inwardly of the first blade tip surface when viewed in the radial direction. A scroll-type machine. 32. The scroll type machine according to claim 81, wherein the second blade tip surface is entirely W from the surface of the end plate.
A scroll-type machine arranged at a distance greater than the first wing tip surface. 8B. A scroll-type machine according to claim 21, comprising means for forming a discharge boat passing through the end plate at its center. 34. A scroll type machine according to claim 21, which comprises means for forming a groove in the center of the end plate O85, fj:'fClaim 21 3. The scroll type machine according to item 1, wherein the first blade tip surface and the second blade tip surface are connected to each other by an intermediate concave transition surface. 86.% The scroll type machine according to claim 21, wherein the first blade tip surface and the second blade tip surface are mutually connected to each other by an intermediate conical transition surface. A scroll type machine according to claim 86, wherein the central axis of the conical transition surface is parallel to the first axis. The scroll-type machine according to claim 21, wherein the first blade tip surface and the second blade tip surface have an intermediate cylindrical transition. Scroll type, wherein the transition surfaces are connected to each other by surfaces, and each intersection of the transition surface and the first blade tip surface and the second blade tip surface has a rounded cross-sectional shape. machine. 39. A scroll type machine according to claim 38, wherein the axis of the cylindrical transition surface is set to 11.
] A scroll-type machine with a thousand lines on the lth axis. 40.% The nuclear machine according to claim 1, wherein the first scroll member is disposed between a first end plate and a spiral first true metal deflection; The second scroll member is disposed on the second end plate and is provided with a spiral second blade, and both scroll members are meshed with each other and can rotate relative to each other around one axis. The above-mentioned end plates and the other end plates are arranged parallel to each other and perpendicular to the axis J: 1 ft.
and a movable chamber having the shape of #20 and having at least one sealed movable chamber between the two wings, whose volume can be continuously changed by relative rotation between the first wing and the second wing. and a volume ratio increasing means provided on at least one of the first and second end plates, the volume ratio increasing means being configured to form a part of the movement cycle. Volume ratio increasing means for reducing the axial spacing between the first and second end plates in the region between which the movable chamber is positioned to still change the volume of the movable chamber; A scroll-type machine equipped with 41. A scroll type machine according to claim 40, wherein the first blade and the second blade are formed to be equal to each other. 42. The scroll-type machine according to claim 40, wherein each of the first blade and the second blade has a functional length extending over a range of at least 900 degrees in the helical direction. Scroll type machine with. 48,9 A scroll-type machine according to claim 40, comprising the above-mentioned volume ratio increasing means and the above-mentioned first
and a second end plate. 44. Scroll-type machine according to claim 40, characterized in that said volume ratio increasing means is arranged inoperative during the initial part of the travel cycle. 45, Patent 40. A scroll type machine according to claim 40, wherein the above-mentioned volume ratio increasing means is provided. , a scroll-type machine configured to be inactive during the first 360 degrees of relative pivot angle between the first and second scroll members during each travel cycle.