JP2020186659A - Scroll type fluid machine - Google Patents

Abstract

To provide a scroll type fluid machine in which end surfaces of an abutment portion are pressed against each other, and which can improve sealing performance and maintains high reliability without deteriorating productivity, even when any of thermal expansion and thermal contraction occurs on a face seal.SOLUTION: A scroll type fluid machine has a fixed scroll, a swiveling scroll disposed oppositely to the fixed scroll, and a face seal that seals an operation chamber on a suction side formed by the fixed scroll and the swiveling scroll. The face seal 26 configures an abutment portion 28 in a circumferential direction entirely by curved surfaces, has a first end surface on one side of the curved surface and a second end surface configured by a curved surface corresponding to the first end surface, and opposes the first end surface to the second end surface.SELECTED DRAWING: Figure 2

Description

The present invention relates to a scrolling fluid machine.

The scroll type fluid machine has a fixed scroll and a swivel scroll arranged to face the fixed scroll, and compresses the fluid by a compression chamber formed by the fixed scroll and the swivel scroll. A face seal is provided on the outer edge of the compression chamber to prevent dust and the like from entering the compression chamber. In addition, the face seal is provided with a joint portion to absorb expansion and contraction due to heat. On the other hand, when operating in an environment where a large amount of dust is present in the surroundings, the dust is mixed into the compression chamber from the abutment portion of the face seal. When dust is mixed into the compression chamber, it increases the wear of the seal member in the compression chamber, shortens the service life, and causes a failure. Therefore, the sealing property of the joint portion of the face seal is important.

As background technology related to this technical field, there are, for example, Patent Document 1 and Patent Document 2. Patent Document 1 describes a scroll-type fluid machine in which a joint portion is formed in a face seal in order to cope with shrinkage due to heat. Further, Patent Document 2 describes a scroll type fluid machine in which a joint portion of a dustproof seal is formed by an oblique line.

Japanese Unexamined Patent Publication No. 2003-42077 WO2018 / 066615

In the scroll type fluid machine disclosed in Patent Document 1, the joint portion of the face seal is formed by a straight line and a concentric arc. Therefore, the end of the face seal only moves in the circumferential direction when it is thermally expanded or contracted, and a gap is provided in the radial direction and the width direction in consideration of expansion, so that the joint portion can be sealed. There is a problem that the sealing property in the radial direction and the width direction is insufficient.

Further, Patent Document 2 has a structure in which the abutment portion of the dustproof seal is formed by diagonal lines or a structure in which a widening portion composed of straight lines is provided. That is, when the abutment portion of the dust-proof seal is formed with diagonal lines, the ends of the dust-proof seal are pressed against each other when thermally expanded, but heat shrinkage occurs at the end in a cold environment. There is a problem that the parts move in a direction away from each other and the sealing property is lost. In addition, in the structure in which the widening portion is provided in the abutment portion, the opposing surfaces of the abutment portion have different shapes, which makes processing difficult and increases the production cost, and improves the sealing performance by lengthening the leakage passage. Similar to Patent Document 1, there is a problem that the sealing property in the radial direction and the width direction for sealing the abutment portion is insufficient.

In view of the above problems, the present invention makes it possible to improve the sealing property of the abutment portion regardless of whether the face seal undergoes thermal expansion or contraction, and is a highly reliable scroll type fluid without impairing productivity. The purpose is to provide a machine.

In view of the above background techniques and problems, the present invention seals an operating chamber formed by a fixed scroll, a swivel scroll arranged to face the fixed scroll, and the fixed scroll and the swivel scroll, to give an example. A scroll-type fluid machine having a face seal, the face seal has a first end face formed of a curved surface and a second end face formed of a curved surface corresponding to the first end face. However, the configuration is such that the first end face and the second end face face each other.

According to the present invention, regardless of whether the face seal undergoes thermal expansion or thermal contraction, the end faces of the abutment portion press against each other, so that the sealing property can be improved and the reliability is maintained without lowering the productivity. High scroll type fluid machinery can be provided.

It is sectional drawing of the scroll type fluid machine in Example 1. FIG. It is a front view of the fixed scroll in Example 1. FIG. It is an enlarged view of the joint portion of the face seal in Example 1. FIG. It is an enlarged view of the joint portion at the time of thermal expansion in Example 1. It is an enlarged view of the abutment portion at the time of heat shrinkage in Example 1. It is an enlarged view of the joint portion of the face seal in Example 2. FIG. It is an enlarged view of the joint portion of the face seal in Example 3. It is an enlarged view of the joint portion of the face seal in Example 4. It is an enlarged view of the joint portion of the face seal in Example 5. It is an enlarged view of the joint part of the face seal in the prior art.

Hereinafter, as the scroll type fluid machine in the embodiment of the present invention, a scroll type air compressor will be taken as an example and will be described in detail with reference to the drawings. In each figure for explaining the embodiment, the same components are designated by the same reference numerals, and the repeated description thereof will be omitted. The working fluid sucked into the working chamber corresponding to the compressor chamber of the compressor may be a specific gas such as nitrogen or oxygen or other mixed gas other than air, or a gas such as vapor and a liquid. Any compressible fluid such as a mixture may be used. Further, the type of machine is not limited to the compressor, and the present invention can be generally used for fluid machines such as pumps, blowers, vacuum pumps, refrigerators, and expanders.

FIG. 1 is a cross-sectional view of the scroll type air compressor in this embodiment. As shown in FIG. 1, the casing 1 of the scroll type air compressor is formed in a tubular shape, is provided on the outside of the swivel scroll 8, and rotatably supports the drive shaft 15 inside the casing 1.

The fixed scroll 2 provided on the opening side of the casing 1 has a mirror plate 3 formed in a substantially disk shape centered on the axis OO and a spiral erected axially on the tooth bottom surface of the mirror plate 3. It is roughly composed of a shaped wrap portion 4, a tubular outer peripheral wall portion 5 provided on the outer diameter side of the end plate 3 surrounding the wrap portion 4, and a plurality of cooling fins 6 projecting from the back surface of the end plate 3. It is configured.

Here, when the innermost diameter end is the winding start end and the outermost diameter end is the winding end end, for example, the wrap portion 4 has a spiral shape from the inner diameter side to the outer diameter side, for example, four turns before and after. It is being wound. The tooth tip surface of the lap portion 4 is separated from the tooth bottom surface of the end plate 9 of the swivel scroll 8 which is the counterpart by a predetermined axial dimension.

Further, seal grooves 4A and 4B are provided on the tooth tip surface of the wrap portion 4 along the winding direction of the wrap portion 4, and the seals in the seal grooves 4A and 4B are in sliding contact with the end plate 9 of the swivel scroll 8. Chip seals 7A and 7B as members are provided. Further, the outer peripheral wall portion 5 has a substantially circular shape and is open to the end surface of the fixed scroll 2. The outer peripheral wall portion 5 is arranged on the outer side in the radial direction of the lap portion 10 in order to avoid interference with the lap portion 10 of the swivel scroll 8.

The swirl scroll 8 provided so as to be swivel in the casing 1 is erected on a substantially disk-shaped end plate 9 arranged to face the end plate 3 of the fixed scroll 2 and a tooth bottom surface of the end plate 9. It is roughly composed of a spiral wrap portion 10 and a plurality of cooling fins 11 projecting from the back surface of the end plate 9. A back plate 12 connected to the drive shaft 15 is provided on the tip end side of the cooling fin 11.

Here, the wrap portion 10 has a spiral shape of, for example, about 3 turns, in substantially the same manner as the wrap portion 4 of the fixed scroll 2. The tooth tip surface of the wrap portion 10 is separated from the tooth bottom surface of the end plate 3 of the fixed scroll 2 which is the counterpart by a predetermined axial dimension. Further, seal grooves 10A and 10B are provided on the tooth tip surface of the wrap portion 10 along the winding direction of the wrap portion 10, and the seals in the seal grooves 10A and 10B are in sliding contact with the end plate 3 of the fixed scroll 2. Chip seals 13A and 13B as members are provided.

Further, on the center side of the back plate 12, a tubular boss portion 14 connected to the crank portion 15A of the drive shaft 15 via the swivel bearing 14a and the bearing housing 14b is integrally formed. At this time, a pulley 15B is provided on one end side of the drive shaft 15 located outside the casing 1, and the pulley 15B is, for example, a belt on the output side of the electric motor as a drive source (neither is shown). It is connected via etc. As a result, the drive shaft 15 is rotationally driven by an electric motor or the like, and the swivel scroll 8 is swiveled with respect to the fixed scroll 2.

Further, a cooling fan 16 is attached to the pulley 15B by using bolts or the like, and the cooling fan 16 generates cooling air in the fan casing 17. As a result, the cooling fan 16 blows the cooling air to the inside of the casing 1 and the back side of the fixed scroll 2 and the swivel scroll 8 along the duct and the like in the fan casing 17, and the casing 1, the fixed scroll 2, the swivel scroll 8 and the like are blown. To cool.

Further, between the back plate 12 and the casing 1, for example, three auxiliary cranks 18 (only one is shown) as rotation prevention mechanisms for preventing the rotation of the swivel scroll 8 are provided. The auxiliary crank 18 is arranged in the auxiliary crank boss portions 18c and 18d formed on the casing 1 and the back plate 12, respectively, via the auxiliary crank bearings 18a and 18b.

The plurality of compression chambers 19 provided between the fixed scroll 2 and the swivel scroll 8 are located between the lap portions 4 and 10 and are sequentially formed from the radial outer side to the radial inner side, and the chip seals 7A, 7B, It is kept airtight by 13A and 13B. Then, each compression chamber 19 is continuously reduced between the lap portions 4 and 10 while moving from the radial outer side to the radial inner side when the swivel scroll 8 swivels in the forward direction. To.

As a result, outside air is sucked into the compression chamber 19A located on the radial outer side of each compression chamber 19 from the suction port 20 described later, and this air reaches the compression chamber 19B located on the radial inner side. It is compressed into compressed air. Then, this compressed air is discharged from the discharge port 22 and stored in an external storage tank (not shown).

The suction port 20 provided on the outer diameter side of the fixed scroll 2 opens from the outer diameter side of the end plate 3 to the outer peripheral wall portion 5 and communicates with the compression chamber 19A located on the outer side in the radial direction. Further, the suction port 20 is located on the radial outside of the lap portion 10 of the swivel scroll 8 in the end plate 3 of the fixed scroll 2, and is opened in a range (non-sliding region) where the tip seal 13B does not slide. .. Then, the suction port 20 sucks air at atmospheric pressure, for example, through a suction filter 21 into a compression chamber 19A located on the outer side in the radial direction.

The suction port 20 may be configured to suck in pressurized air. In this case, the suction filter 21 may be removed and the suction port 20 may be connected to the pipe to which the pressurized air is supplied.

The discharge port 22 provided on the radial inner side (center side) of the end plate 3 of the fixed scroll 2 communicates with the compression chamber 19B located on the radial inner side, and discharges the compressed air in the compression chamber 19B to the outside. Is.

The flange 24 located radially outside the wrap portion 4 of the fixed scroll 2 fixes the fixed scroll 2 to the casing 1 by the flange 1a portion of the casing 1. The positioning of the fixed scroll 2 and the casing 1 is performed by inserting a positioning member through the positioning hole 27.

The face seal groove 25 provided on the end surface of the fixed scroll 2 facing the end surface 9 of the swivel scroll 8 is located on the radial outer side of the outer peripheral wall portion 5 and is formed in an annular shape surrounding the outer peripheral wall portion 5. .. Further, an annular face seal 26 is installed in the face seal groove 25. The face seal 26 airtightly seals between the end face of the fixed scroll 2 and the end surface 9 of the swivel scroll 8 to prevent dust and the like from entering the outer peripheral wall portion 5 from between them.

Next, the operation of the scroll type air compressor in this embodiment will be described. First, when the drive shaft 15 is rotationally driven by a drive source (not shown) such as an electric motor, the swivel scroll 8 is centered on the axis OO of the drive shaft 15 in a state where the rotation is prevented by the rotation prevention mechanism. The rotating motion is performed, and the compression chamber 19 defined between the lapping portion 4 of the fixed scroll 2 and the lapping portion 10 of the swivel scroll 8 is continuously reduced. As a result, the air sucked from the suction port 20 of the fixed scroll 2 can be sequentially compressed in each compression chamber 19 and discharged as compressed air from the discharge port 22 of the fixed scroll 2 toward an external tank (not shown). it can.

Next, the cooling structure of the scroll type air compressor in this embodiment will be described. The cooling air generated by the cooling fan 16 circulates inside the casing 1 and on the back side of the scrolls 2 and 8 along the duct and the like in the fan casing 17, and cools the casing 1, the fixed scroll 2, the swivel scroll 8, and the like. To do.

Therefore, in a dust environment in which a large amount of dust is present around the scroll type compressor, the dust rides on the cooling air and reaches the fixed scroll 2 and the swivel scroll 8. Therefore, it is important to seal between the end face of the fixed scroll 2 and the end face 9 of the swivel scroll 8 with the face seal 26.

FIG. 2 is a front view of the fixed scroll 2 in this embodiment. In FIG. 2, since the face seal 26 needs to be made of a material having excellent wear resistance and slidability, it usually has a higher coefficient of linear expansion than that of the fixed scroll 2. Therefore, during the compression operation or in a cold environment such as below freezing point, a difference in thermal expansion or a difference in thermal contraction occurs between the face seal 26 and the fixed scroll 2. Therefore, the face seal 26 is provided with a joint portion 28 in order to absorb expansion and contraction due to heat. If the abutment portion 28 is not provided, tension is generated between the face seal 26 and the face seal groove 25 due to the difference in the amount of thermal deformation, the face seal 26 is distorted, and the sealing performance is deteriorated.

FIG. 3 is an enlarged view of the abutment portion 28 of the face seal 26 in FIG. As shown in FIG. 3, in this embodiment, all the abutment portions 28 are formed of curved surfaces. That is, the abutment portion 28 of the face seal 26 is composed of the first end face EF1 shown by the curve a1-a2 and the second end face EF2 shown by the curve b1-b2. The curve a1-a2 of the first end face EF1 has a surface c1 protruding outward in the radial direction of the face seal 26, and the curve b1-b2 of the second end face EF2 protrudes inward in the radial direction of the face seal 26. It has surface c2. The protrusion amounts wc1 and wc2 of the surfaces c1 and c2 are indicated by wc1> (w-wc2) and wc2> (w-wc1), where w is the width of the face seal 26.

In other words, the thickness of the first end face EF1 in the radial direction, that is, the radial direction of the annular ring is different in the circumferential direction of the annular ring. Further, as shown in FIG. 3, the first end face EF1 has a first region R1 from the inner peripheral side to the outer peripheral side in the radial direction of the annular ring and the diameter of the annular ring. The second region R2 from the outer peripheral side to the inner peripheral side in the direction and the third region R3 from the inner peripheral side to the outer peripheral side in the radial direction of the annular ring are from the tip to the center of the face seal 26. Exists towards. Further, the face seal 26 has a first end face formed of a curve and a first end face formed of a curve corresponding to the first end face when viewed from a direction orthogonal to the radial direction of the annular ring. It has two end faces, and the first end face and the second end face are arranged so as to face each other.

Next, the characteristics of the sealing function of the abutment portion 28 in this embodiment will be described in comparison with the abutment portion 28 having the conventional structure shown in FIG. As shown in FIG. 10, the conventional abutment portion 28 has a straight line e1-e2 and a first end face EF1 composed of a curved line e2-e3 having an arc concentric with the outer diameter or inner diameter of the face seal 26 and a straight line e3-e4. , The straight line e5-e6, the concentric arc curve e6-e7, and the second end face EF2 composed of the straight line e7-e8. In the conventional structure, when the temperature of the fixed scroll 2 and the face seal 26 rises due to the compression operation and thermal expansion occurs, the abutment portion 28 of the face seal 26 follows a concentric arc of the outer diameter or the inner diameter of the face seal 26. (Arrows f1 and f2 in FIG. 10). Until the first end face EF1 reaches the second end face EF2 due to thermal expansion, there is a gap between the first end face EF1 and the second end face EF2, and dust enters the compression chamber through the gap. It will reach. Further, the gap between the first end face EF1 and the second end face EF2 is designed so that the gap disappears when the scroll type air compressor reaches the maximum temperature in use, so that there is a gap in the meantime. It will be in the open state. Further, since the inside of the face seal 26 in the radial direction communicates with the suction port, a negative pressure is generated during operation and the second end face EF2 is attracted to the first end face EF1, and the respective curves e2-e3 and curves. It is conceivable that the e6 to e7 are in contact with each other, but the sealing property is insufficient in a dust environment where a large amount of dust is present.

FIG. 4 is an enlarged view of the abutment portion 28 at the time of thermal expansion in this embodiment. As shown in FIG. 4, it extends along the concentric arcs of the outer diameter or inner diameter of the face seal 26 in the directions of arrows f1 and f2 due to thermal expansion. After reaching the end point b2 of the second end face EF2, the end point a1 of the first end face EF1 slips between the inner diameter 26a of the face seal 26 and the inner wall 25a of the face seal groove 25 when the thermal expansion further progresses. The first end face and the second end face are pressed against each other to exhibit a strong sealing property. Further, after the end point b1 of the second end face EF2 reaches the end point a2 of the first end face EF1, the end point b1 is similarly inserted between the outer diameter 26b of the face seal 26 and the outer wall 25b of the face seal groove 25 and sandwiched. The second end face EF2 and the first end face EF1 press against each other to exhibit a strong sealing property. Then, the first end face EF1 reaches the second end face EF1 due to thermal expansion, and then the respective end points a1 and b1 are sandwiched between the inner wall 25a and the outer wall 25b, so that the temperature range is wider than that of the conventional structure. It can exhibit sealing properties. In particular, since the first end face EF1 and the second end face EF2 are formed of curved surfaces, they move smoothly while being in contact with each other, so that the sealing property can always be improved. Further, since it is formed of a curved surface, the dimensional change of the abutment portion 28 is small, stress concentration does not occur, and the strength is also excellent. Further, when viewed in the axial direction, the sealing property is higher than the surface contact because the line contact is obtained.

Next, the characteristics of the sealing function of this embodiment in a cold environment such as below freezing point will be described in comparison with the joint portion 28 of the conventional structure shown in FIG. As shown in FIG. 10, in the conventional structure, heat shrinkage occurs in a cold environment, and the first end face EF1 faces in the direction indicated by the arrow g1 and the second end face EF2 faces in the direction indicated by the arrow g2. It contracts along an arc concentric with the outer or inner diameter of 26. Therefore, the gap between the first end face EF1 and the second end face EF2 widens and the sealing performance deteriorates.

FIG. 5 is an enlarged view of the abutment portion 28 at the time of heat shrinkage in this embodiment. As shown in FIG. 5, the first end face EF1 shrinks in the direction of arrow g1 and the second end face EF2 shrinks in the direction of arrow g2 due to heat shrinkage. At that time, they are in strong contact with each other at the contact points h of the base portions of the protruding portions c1 and c2. Since the first end face EF1 and the second end face EF2 are formed of a curved surface, the contact point h moves in the g1 or g2 direction so as to slide on the curved surface depending on the amount of heat shrinkage, or the contact range increases due to elastic deformation. Or something. Although the contact point h moves depending on the amount of heat shrinkage, it is always in contact with the contact point h and can always exhibit a sealing property during movement.

Further, the first end face EF1 and the second end face EF2 of this embodiment have shapes corresponding to each other, and can be easily formed by, for example, cutting the annular face seal 26 with a blade having the same shape as the end face. There is also the effect of being able to do it.

As described above, according to the present embodiment, when the face seal is thermally expanded or contracted, the sealing property of the abutment portion can be improved in either case, so that the reliability of the compressor can be improved. Furthermore, since it is easy to process, it does not deteriorate the productivity.

FIG. 6 is an enlarged view of the abutment portion 28 of the face seal 26 in this embodiment. As shown in FIG. 6, in the present embodiment, the abutment portion 28 is entirely formed of a curved surface, the first end surface EF1 has a plurality of radially outwardly protruding surfaces i1 and i2, and the second end surface EF2. Has a plurality of surfaces i3 and i4 protruding inward in the radial direction.

By providing a plurality of protruding surfaces, the number of points of contact at the time of thermal expansion or contraction increases as compared with Example 1, and the sealing property is improved. In addition, since the leakage passage is long and complicated, the intrusion of dust can be reduced.

In FIG. 6, the number of protruding surfaces is two, but two or more may be used. When two or more are used, the sealing property can be further improved.

As described above, according to the present embodiment, the sealing property of the abutment portion can be further improved when the face seal 26 is thermally expanded or contracted, and the reliability of the scroll type air compressor is further improved. Can be made to.

FIG. 7 is an enlarged view of the abutment portion 28 of the face seal 26 in this embodiment. As shown in FIG. 7, in this embodiment, the abutment portion 28 is entirely formed of a curved surface, the first end surface EF1 has a surface c1 protruding radially outward, and the second end surface EF2 is radially inside. It has a surface c2 protruding from the surface. Then, the protrusion amount wc2 of the second end face EF2 is made smaller than the protrusion amount wc1 of the first end face EF1. In FIG. 7, wc1> wc2 is set, but wc1 <wc2 may be set. That is, by making a difference in the protruding amount of the first end face EF1 and the second end face EF2, the strength of the end face having the smaller protruding amount is lowered as compared with the end face having the larger protruding amount, and the deformation is made easier. Therefore, in this embodiment, the sealing property of the abutment portion 28 is further improved.

FIG. 8 is an enlarged view of the abutment portion 28 of the face seal 26 in this embodiment. As shown in FIG. 8, in the present embodiment, the abutment portion 28 is entirely formed of a curved surface, and the radius Rki of the inner wall 25a of the face seal groove 25 and the radius Rfi of the inner diameter 26a of the face seal 26 are Rki> Rfi.

By setting Rki> Rfi, it is necessary to pull and attach the face seal 26 when assembling the face seal 26 to the face seal groove 25. Therefore, before the face seal 26 is thermally deformed by a compression operation or the like, the face seal 26 is formed at the abutment portion 28. The first end face and the second end face come into contact with each other, and the sealing property of the abutment portion 28 can be improved.

Further, the radius Rko of the outer wall 25b of the face seal groove 25 and the radius Rfo of the outer diameter 26b of the face seal 26 may be set to Rko <Rfo. Even when Rko <Rfo, the first end face and the second end face come into contact with each other at the abutment portion 28 before the face seal 26 is thermally deformed, so that the sealing property of the abutment portion 28 can be improved.

As described above, in this embodiment, the sealing property of the abutment portion 28 can be improved even when there is no or small thermal deformation.

FIG. 9 is an enlarged view of the abutment portion 28 of the face seal 26 in this embodiment. As shown in FIG. 9, in this embodiment, the fixed scroll 2 is provided with the second face seal groove 29, and the second face seal 30 is provided in the second face seal groove 29.

Further, the joint portion 28 of the face seal 26 and the second face seal 30 is composed of a first end face EF1 formed of a curved surface and a second end face EF2 corresponding thereto. The curvatures of the first end face EF1 and the second end face EF2 of the face seal 26 and the curvatures of the first end face EF1 and the second end face EF2 of the second face seal 30 are different.

For example, the curvature of the first end face EF1 and the second end face EF2 of the face seal 26 is reduced so that the effect is exhibited even when the temperature rise is small, and the first end face EF1 of the second face seal 30 is designed. In this embodiment, the sealing property can be improved in a wider temperature range by increasing the curvature of the second end face EF2 and designing the second end face EF2 so as to exert an effect when the temperature rise is large.

In the description of this embodiment, the number of face stickers is two, but a plurality of face stickers may be used. By installing a plurality of them, the sealing property can be improved in a wider temperature range.

Although the examples have been described above, the present invention is not limited to the above-described examples, and various modifications are included without departing from the technical idea or the main features thereof. For example, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to those having all the described configurations. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment.

1: Casing, 2: Fixed scroll, 8: Swirling scroll, 19: Compression chamber, 20: Suction port, 22: Discharge port, 25: Face seal groove, 25a: Inner wall of face seal groove, 25b: Outer wall of face seal groove , 26: Face seal, 26a: Inner diameter of face seal, 26b: Outer diameter of face seal, 28: Abutment, 29: Second face seal groove, 30: Second face seal

Claims (10)

Fixed scroll and
A swivel scroll arranged facing the fixed scroll and
It has a face seal that seals the working chamber formed by the fixed scroll and the swivel scroll.
The face seal has a first end face made of a curved surface and a second end face made of a curved surface corresponding to the first end face.
A scroll-type fluid machine characterized in that the first end face and the second end face face each other. The scroll type fluid machine according to claim 1.
The face seal is formed in an annular shape, the curved surface of the first end face has a surface protruding outward in the radial direction of the annular ring, and the curved surface of the second end face is the annular shape. A scroll-type hydraulic machine characterized by having a surface protruding inward in the radial direction of the annulus. The scroll type fluid machine according to claim 2.
The face seal is arranged in the annular face seal groove provided on the fixed scroll.
The radial width of the face seal groove is w, the protruding amount of the surface protruding outward in the radial direction of the first end face is wc1, and the protruding amount of the surface protruding inward in the radial direction of the second end face is wc2. A scroll-type fluid machine characterized in that it has a relationship of wc1> (w-wc2) and wc2> (w-wc1). The scroll type fluid machine according to claim 2.
The first end surface has a plurality of surfaces protruding outward in the radial direction.
A scroll-type fluid machine in which the second end surface has a plurality of surfaces protruding inward in the radial direction. The scroll type fluid machine according to claim 2.
A scroll-type fluid machine characterized in that the amount of protrusion of the first end face protruding outward in the radial direction and the amount of protrusion of the surface of the second end face protruding inward in the radial direction are different. The scroll type fluid machine according to claim 2.
The face seal is arranged in the annular face seal groove provided on the fixed scroll.
The radius of the radial inner wall of the face seal groove is Rki, the radius of the radial inner diameter of the face seal is Rfi, the radius of the radial outer wall of the face seal groove is Rko, and the radius of the radial outer diameter of the face seal is Rfo. When, a scroll type fluid machine having a relationship of Rki> Rfi or Rko <Rfo. The scroll type fluid machine according to claim 1.
The face seal is arranged in the annular face seal groove provided on the fixed scroll.
A scroll-type fluid machine having a plurality of the face seal and the face seal groove. Fixed scroll and
A swivel scroll arranged facing the fixed scroll and
It has a face seal that seals the working chamber formed by the fixed scroll and the swivel scroll.
The face seal has a first end face and a second end face corresponding to the first end face, and the first end face and the second end face are arranged in an annular shape so as to face each other. Ori,
The first end face is a scroll type fluid machine characterized in that the radial thickness of the annular ring is different in the circumferential direction of the annular ring. Fixed scroll and
A swivel scroll arranged facing the fixed scroll and
It has a face seal that seals the working chamber formed by the fixed scroll and the swivel scroll.
The face seal has a first end face formed of a curved surface and a second end face formed of a curved surface corresponding to the first end face, and the first end face and the second end face are formed. They are placed facing each other
The first end face has a first region from the radial inner peripheral side of the annular ring to the outer peripheral side, and the annular ring from the radial outer peripheral side to the inner peripheral side. A scroll-type hydraulic machine characterized in that a second region facing the face seal exists from a tip portion to a center portion of the face seal. Fixed scroll and
A swivel scroll arranged facing the fixed scroll and
It has a face seal that seals the working chamber formed by the fixed scroll and the swivel scroll.
The face seal is formed in an annular shape, and when viewed from a direction orthogonal to the radial direction of the annular ring, the first end face formed of a curved line corresponds to the first end face. Has a second end face composed of curved lines
A scroll-type fluid machine characterized in that the first end face and the second end face are arranged so as to face each other.

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