JPH06272680A - Scroll type fluid machinery - Google Patents

Abstract

(57) [Abstract] [Purpose] A seal member effectively seals between the tooth top surface of the lap portion and the tooth bottom of the other side, thereby prolonging the life of the seal member and improving reliability. A wrap portion 29 of an orbiting scroll 27 is formed such that a height dimension H from a tooth bottom 28A to a tooth tip surface 29A of an end plate 28 is gradually increased from an inner peripheral side to an outer peripheral side. A concave groove 29B extending from the outer peripheral side to the inner peripheral side of the wrap portion 29 is formed on the surface 29A. And
The inner peripheral portion 43A of the seal member 43 is fitted and fixed on the inner peripheral side of the concave groove 29B, and the inner peripheral portion 4 is formed on the outer peripheral side of the concave groove 29B.
The outer peripheral portion 43B connected to 3A through the connecting portion is provided with the concave groove 2
9B is inserted so that it can be floated. Also,
The seal member 44 of the fixed scroll 34 is also configured in the same manner.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine suitable for use in, for example, an air compressor or a vacuum pump.

[0002]

2. Description of the Related Art FIGS. 4 to 7 show a scroll type air compressor as a scroll type fluid machine according to the prior art.

In the drawings, reference numeral 1 denotes a drive shaft rotatably provided in a casing (not shown), and a tip side thereof is a crank 1A. Reference numeral 2 denotes an orbiting scroll rotatably supported by the crank 1A of the drive shaft 1. The orbiting scroll 2 has an end plate 3 formed in a disk shape, and a spiral wrap portion 4 erected from the tooth bottom 3A of the end plate 3 on the center side as a winding start end and the outer peripheral side as a winding end end. The mirror plate 3 is generally composed of a boss portion 5 provided at the center of the rear surface side. Here, as shown in FIG. 6, the lap portion 4 has a groove 4B extending from the outer peripheral side to the inner peripheral side of the lap portion 4 along the tooth top surface 4A.
Is formed, and a seal member 7, which will be described later, is fitted in the concave groove 4B so as to be floatable. The crank 1A of the drive shaft 1 is rotatably mounted in the boss 5 via a swivel bearing 6.

Reference numeral 7 denotes a seal member provided in the concave groove 4B of the wrap portion 4. The seal member 7 is formed in a string shape having a substantially square cross section as shown in FIG. Is loosely fitted over the entire circumference with a gap.

Reference numeral 8 denotes a fixed scroll fixed to the casing so as to face the orbiting scroll 2, and the fixed scroll 8 is a disk arranged so that its center coincides with the axis O1-O1 of the drive shaft 1. -Shaped end plate 9, a spiral wrap portion 10 standing upright from the tooth bottom 9A of the end plate 9 in the same manner as the wrap portion 4 of the orbiting scroll 2, and located on the outer peripheral side of the end plate 9, and the wrap portion 10 And a supporting portion 11 formed in a tubular shape so as to surround the.

Here, in the wrap portion 10, as in the wrap portion 4 of the orbiting scroll 2, the concave groove 1 is formed in the tooth top surface 10A.
0B is formed, and the seal member 7 is formed in the groove 10B.
A seal member 12 similar to that is loosely fitted around the entire circumference with a gap.

Each of the scrolls 2 and 8 thus constructed has an axis O of the orbiting scroll 2 as shown in FIG.
With the 2-O2 eccentric with respect to the axis O1-O1 of the fixed scroll 8 by a distance .delta., The wrap portion 4 of the orbiting scroll 2 is offset from the wrap portion 10 of the fixed scroll 8 by a predetermined angle so as to overlap with each other. Is installed in. Thus, when the orbiting scroll 2 is orbited with respect to the fixed scroll 8, a plurality of compression chambers 13, 13, ... Which are continuously reduced are defined between the respective wrap portions 4, 10.

Reference numerals 14 and 15 denote a suction port and a discharge port formed in the fixed scroll 8, and the suction port 1
4 is provided on the outer peripheral side of the end plate 9 so as to communicate with the compression chamber 13 on the outermost peripheral side, and the discharge port 15 is the compression chamber 1 on the outermost center side.
It is provided at the center of the end plate 9 so as to communicate with the end plate 3.

The scroll type air compressor according to the prior art has the above-mentioned structure, and its operation will be described below.

First, the drive shaft 1 is driven by a motor (not shown).
When the rotary drive is performed, this rotation causes the crank 1 of the drive shaft 1 to rotate.
A is transmitted from A to the orbiting scroll 2 via the orbiting bearing 6, whereby the orbiting scroll 2 is fixed to the fixed scroll 8
Around the axis O1 -O1 of, the turning motion is performed with a turning radius of a distance δ.

Here, the compression chambers 13, 13, ... Defined between the wrap portions 4, 10 are continuously reduced by this swiveling motion, and the air sucked from the suction port 14 is compressed in each compression chamber 13. By sequentially compressing, the compression chamber 13 on the center side
The higher the pressure, the more the concave grooves 4B, 10B of the wraps 4, 10
The seal members 7 and 12 provided inside are pressed from the inside to the outer peripheral surfaces of the recessed grooves 4B and 10B by the pressure of compressed air, and the pressure of this air causes the seal members 7 and 12 to be removed from the inside of the recessed grooves 4B and 10B. As shown in FIG.
9 of the wrap portions 4, 10 of the orbiting scroll 2 and the fixed scroll 8 and the tooth top surface 4A, 10A and the tooth bottom 3A,
Airtightly seal between 9A.

The compression chambers 13, 13, ... Defined between the wrap portions 4, 10 are continuously contracted by this turning motion, and the air sucked from the suction port 14 is compressed in each compression chamber 13. The compressed air is discharged from the discharge port 15 to an external air tank (not shown) or the like while being sequentially compressed.

[0013]

By the way, in the above-mentioned prior art, since the compression heat is generated in each compression chamber 13 between the orbiting scroll 2 and the fixed scroll 8 at the time of the compression action, the compression heat is generated by this compression heat. The scrolls 2, 8
Becomes hot. Moreover, since the pressure gradually increases from the outer peripheral side compression chamber 13 to the central side compression chamber 13, the lap portions 4 and 10 are shown in the characteristic line of FIG. 7 from the central side to the radially outer side. Such a temperature gradient occurs.

That is, the compression chamber 13 on the center side becomes higher in temperature than the compression chamber 13 on the outer peripheral side, and when the discharge pressure reaches the discharge pressure during the rated operation, for example, a pressure of about 0.83 MPa, each scroll 2, The temperature of the center side of 8 rises to 200 ° C. or higher.

Therefore, in the prior art, each wrap portion 4,
The center side of 10 thermally expands, and the inner peripheral side portions of the seal members 7 and 12 are strongly pressed against the tooth bottoms 3A and 9A of the end plates 3 and 9 without floating from the concave grooves 4B and 10B. There is a problem in that the inner peripheral side portion may be worn early due to strong sliding contact with the tooth bottoms 3A and 9A, and the sealing performance may be impaired.

The present invention has been made in view of the above-mentioned problems of the prior art, and the present invention can effectively seal between the tooth top surface of each lap portion and the mating tooth bottom by a seal member, An object of the present invention is to provide a scroll type fluid machine capable of improving reliability and extending the life of a seal member.

[0017]

The features of the structure adopted by the present invention to solve the above-mentioned problems are that at least one of the wrap portions of the orbiting scroll and the fixed scroll is provided with teeth of the wrap portion. A concave groove extending from the outer peripheral side to the inner peripheral side of the lap portion is formed along the front surface, and the concave groove is fixed to the concave groove on the inner peripheral side of the lap portion in the concave groove. The spiral seal member is provided on the outer peripheral side so as to float in the groove.

[0018]

With the above structure, even if a clearance is formed in advance between the tooth top of the lap portion and the tooth bottom of the other side, when the orbiting scroll starts the orbiting motion with respect to the fixed scroll, the orbiting scroll is rotated. Alternatively, on the outer peripheral side of the wrap portion of the fixed scroll, the seal member floats from the groove and makes a close sliding contact with the end plate (tooth root) of the other side, so that the fluid can be reliably contained at least in the compression chamber on the outer peripheral side.
It can be compressed to an intermediate pressure.

Since the lap portion on the inner peripheral side is thermally expanded by the compression heat at this time, the dimension from the tooth root to the tooth tip is made small in advance in consideration of this thermal expansion amount, and, for example, the rated value is obtained. During operation, the gap between the inner peripheral lap portion and the mating tooth bottom can be set to an appropriate size, and the seal member fixed to the inner peripheral lap portion can be prevented from being worn or damaged.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described below with reference to FIGS.

In the drawing, reference numeral 21 denotes a casing, 22 denotes a casing main body which constitutes the casing 21 together with a front casing 23 which will be described later, and the casing main body 22 has a disc-shaped bottom portion 22A and an outer peripheral side of the bottom portion 22A which will be described later. 22B extending toward the fixed scroll 34 side of the
And a cylindrical bearing portion 22 formed on the inner peripheral side of the bottom portion 22A.
It is formed from C and in the shape of a stepped cylinder with a bottom.

Reference numeral 23 denotes a cylindrical portion 22 of the casing body 22.
B shows a stepped tubular front casing integrally formed by projecting radially inward from the front end side.
Is located on the inner peripheral side of the orbiting scroll 2 described later.
A thrust receiving portion 23A which is in sliding contact with the back side of the thrust receiving portion 7 to receive the load in the thrust direction, and a plurality of notch portions 23B which are located on the inner peripheral side of the thrust receiving portion 23A and are formed at predetermined intervals in the circumferential direction. , 23B, ... (Only two are shown) are provided.

Reference numeral 24 denotes a bearing portion 22C of the casing body 22.
2 shows a drive shaft rotatably supported via bearings 25 and 26. The front end side of the drive shaft 24 extends into the casing 21 to form a crank 24A, and the axis O3 -O3 of the crank 24A is shown in FIG. As shown in FIG.
It is eccentric by a predetermined dimension d with respect to -O4. The base end side of the drive shaft 24 is connected to an electric motor (not shown) or the like outside the casing 21, and is rotationally driven by this electric motor.

Reference numeral 27 denotes an orbiting scroll which is located inside the casing 21 and is provided so as to be capable of orbiting on the crank 24A of the drive shaft 24. The orbiting scroll 27 is a disk-shaped end plate 28 and the end plate 28. It is composed of a spiral wrap portion 29 provided upright from the tooth bottom 28A and a boss portion 30 described later.

Here, the lap portion 29 has heights H from the tooth bottom 28A to the tooth crest 29A extending from the inner peripheral side to the outer peripheral side thereof, and the dimensions H1, H2, H3, H4, H are respectively obtained.
5, H6, ..., these dimensions H1 to H6 are

[0026]

[Formula 1] H1 <H2 <H3 <H4 <H5 <H6 ... Further, a groove 29B extending from the inner peripheral side to the outer peripheral side is formed along the lap portion 29 in the tooth crest 29A almost in the same manner as the groove 4B described in the above-mentioned prior art.

Here, in the concave groove 29B, the temperature of the wrap portion 29 is, for example, 120 to 130 ° C. as shown by the characteristic line shown in FIG.
In the range where the width of the wrap portion 29 changes abruptly, a range of about 2 turns from the center side of the wrap portion 29 becomes a small width portion 29B1 having a small groove width, and a large portion 29 having a large groove width on the outer peripheral side of the small width portion 29B1.
It is B2.

Reference numeral 30 denotes a boss portion provided in the center of the end plate 28 on the rear surface 28B side, and a crank 24A is mounted in the boss portion 30 via a swivel bearing 31.

Reference numeral 32 denotes a plurality of key grooves 32 provided on the outer peripheral side of the back surface 28B of the end plate 28. The respective key grooves 32 are provided.
Are formed at predetermined intervals in the circumferential direction, and each of the key grooves 32 is formed.
An Oldham's joint 33 as a rotation preventing mechanism is disposed between and the notch 23B of the front casing 23. When the drive shaft 24 is rotationally driven, the orbiting scroll 27 is given a circular motion having a orbiting radius of the dimension d by the crank 24A, and the Oldham coupling 33 prevents rotation of the drive shaft 24. It keeps turning (orbiting) around the axis.

Reference numeral 34 denotes a fixed scroll provided so as to abut the front end surface of the front casing 23 so as to cover the front end side of the casing 21, and the center of the fixed scroll 34 is the axis O4 of the drive shaft 24. -O4, the end plate 35 arranged in the central portion so as to coincide with -O4, and the bottom 35 of the end plate 35
A cylinder that is formed so as to surround the outer peripheral side of the end plate 35 and the spiral lap portion 36 that is erected from A to the orbiting scroll 27, and that abuts the outer peripheral side of the front end surface of the front casing 23. And part 37. The wrap portion 36 of the orbiting scroll 27 has a predetermined angle (for example, 180 degrees) with the wrap portion 36 of the fixed scroll 34.
They overlap each other with a shift of about (°).

Here, the wrap portion 36 of the fixed scroll 34, like the wrap portion 29 of the orbiting scroll 27, has a height dimension from the tooth bottom 35A to the tooth tip surface 36A directed from the inner peripheral side to the outer peripheral side. It is formed so that it gradually increases. Further, the tooth top surface 36A of the wrap portion 36 has a small width portion 36B1 having a small width on the inner peripheral side and a large width on the outer peripheral side, similarly to the concave groove 29B provided in the wrap portion 29 of the orbiting scroll 27. A recessed groove 36B, which has become a large portion 36B2, is formed.

Reference numerals 38, 38, ... Show a plurality of compression chambers defined between the wrap portion 29 of the orbiting scroll 27 and the wrap portion 36 of the fixed scroll 34, and each compression chamber 38 is a wrap of the fixed scroll 34. While the orbiting scroll 27 makes an orbiting motion with respect to the portion 36, the inner volume thereof is gradually reduced. Then, each compression chamber 38 is
When the orbiting scroll 27 orbits, the air is taken in from a suction port 39 described later and the air is sequentially compressed.

Reference numeral 39 denotes a suction port formed in the cylindrical portion 37 of the fixed scroll 34. The suction port 39 is formed between the wrap portion 29 and the wrap portion 36 of the fixed scroll 34 when the orbiting scroll 27 is turned. It is adapted to communicate with the outermost compression chamber 38 formed.

Reference numeral 40 denotes a discharge port formed at the center of the end plate 35 of the fixed scroll 34, and the discharge port 40 communicates with the most central (high pressure side) compression chamber 38.

Reference numeral 41 denotes an oil scraper located inside the casing body 22 and fitted and fixed to the drive shaft 24.
Is disposed so that its tip end side comes into contact with the oil liquid L such as lubricating oil contained in the casing 21. When the drive shaft 24 rotates, the oil scraper 41 scrapes up the oil liquid L to supply the oil liquid L to the bearing 25, the slewing bearing 31, the thrust receiving portion 23A of the front casing 23, and the like.
These are cooled and lubricated. 42 is an oil scraper 4
The counter weight 42 is fixed to the counter weight 1, and the counter weight 42 balances the rotation of the drive shaft 24.

Reference numeral 43 indicates a seal member provided in the concave groove 29B of the wrap portion 29, and the seal member 43 is shown in FIG.
As shown in, the inner peripheral portion 43A and the outer peripheral portion 43B are integrally connected to each other via the connecting portion 43C in the middle of the circumferential direction, and are formed into one spiral shape as a whole. The seal member 43 does not have to be spirally formed in advance, but may be bent in a spiral shape when mounted in the recessed groove 29B.

Since the inner peripheral portion 43A has a high temperature on the inner peripheral side of the wrap portion 29, it is made of a resin material in which a liquid crystal polymer or the like is mixed with a carbon base material so as to have high heat resistance and abrasion resistance. The outer peripheral portion 43B is made of a fluororesin base material so as to have high airtightness and self-lubricating property. Further, the inner peripheral portion 43A and the outer peripheral portion 43B are connected to each other by a connecting portion 43C made of a flexible material so as to be bendable and to prevent air leakage in the radial direction. The inner peripheral portion 43A of the seal member 43 is fixed in the narrow width portion 29B1 of the concave groove 29B with a spiral of about two turns from the center side, and the outer peripheral portion 43B is floatable in the large portion 29B2 of the concave groove 29B. Is attached in a loosely fitted state.

A seal member 44 similar to the seal member 43 is also mounted on the wrap portion 36 of the fixed scroll 34, and the inner peripheral portion 44A thereof has a small width portion 36 of the concave groove 36B.
The outer peripheral portion 44B is fixed in B1 and is mounted in a large portion 36B2 of the concave groove 36B in a loosely fit state so as to be floatable. The inner peripheral portion 44A and the outer peripheral portion 44B are connected by a connecting portion 44C made of a flexible material so that the inner peripheral portion 44A and the outer peripheral portion 44B are bendable and do not leak air in the radial direction.

Incidentally, 45 and 45 are the suction ports 39.
Is a joint pipe for connecting an intake filter to the pipe, 46 is a discharge pipe for guiding the compressed air discharged from the discharge port 40 to an air tank (not shown), 47 is a cooling fan provided on the drive shaft 24, and 48 is the The pulley fixed to the base end side of the drive shaft 24 is shown.

The scroll type air compressor according to the present embodiment has the above-mentioned structure. When the drive shaft 24 is rotationally driven by the electric motor via the pulley 48, the belt, etc., this rotation is caused by the crank 24A and the slewing bearing. It is transmitted to the orbiting scroll 27 via 31. As a result, the orbiting scroll 27 orbits about the axis of the drive shaft 24 with a orbiting radius of a predetermined dimension d, and by this orbiting movement, external air is sucked from the suction port 39 to the outermost compression chamber 3a.
Inhale into 8. Then, each compression chamber 38 is continuously contracted, and the sucked air is sequentially sent to the compression chamber 38 on the inner peripheral side to be compressed, and the compressed air is discharged from the discharge port 40 via the discharge pipe 46 to an external air tank. And so on.

However, in this embodiment, the orbiting scroll 2 is used.
The wrap portion 29 of No. 7 is formed such that the height dimension H from the tooth bottom 28A of the end plate 28 to the tooth tip surface 29A gradually increases from the inner peripheral side to the outer peripheral side, and the groove 29B is formed along the tooth tip surface 29A.
On the other hand, the inner peripheral portion 43A of the seal member 43 is fixed to the inner peripheral side in the concave groove 29B, and the inner peripheral portion 43A is connected to the outer peripheral side of the concave groove 29B via the connecting portion 43C. The formed outer peripheral portion 43B is provided so as to be capable of floating from the concave groove 29B, and the fixed scroll 34 and the seal member 44 are also configured in the same manner as described above, so that the following operational effects are obtained.

That is, when the orbiting scroll 27 and the fixed scroll 34 are abutted against each other, between the tooth top surfaces 29A and 36A of the respective wrap portions 29 and 36 and the tooth bottoms 28A and 35A of the counterpart end plates 28 and 35, respectively. As shown in FIG. 2, a clearance C is formed in the groove so that the dimension gradually increases from the outer peripheral side toward the inner peripheral side. Then, when the orbiting scroll 27 starts the orbiting motion with respect to the fixed scroll 34, on the outer peripheral side of the respective wrap portions 29, 36 of the orbiting scroll 27 and the fixed scroll 34, the seal members 43, 44 of the seal members 43, 44 are inserted from inside the concave grooves 29B, 36B. The outer peripheral portions 43B and 44B float and come into close sliding contact with the counterpart end plates 28 and 35 (tooth bottoms 28A and 35A), so that air can be reliably contained in at least the outer peripheral side compression chamber 38, and this air can be compressed to an intermediate pressure. It can be compressed to a degree.

Since the inner peripheral side of each lap portion 29, 36 rises in temperature due to the compression heat of air and thermally expands as shown in FIG. 7, each lap portion 29, 36 is operated at the rated operation of the air compressor.
Inner peripheral tooth top surfaces 29A and 36A of 36 and the other tooth root 2
The gap C between 8A and 35A can be reduced to an appropriate size to maintain airtightness, and the air compressed to an intermediate pressure by the compression chamber 38 on the outer peripheral side can be further compressed to a desired high pressure in the compression chamber 38 on the inner peripheral side. Can be compressed to a level.

Here, the tooth top surface 2 of each lap portion 29, 36
In 9A and 36A, since the temperature rises sharply toward the inner peripheral side of the wrap portions 29 and 36, and the height dimension H is formed to be smaller toward the inner peripheral side in view of the large thermal expansion of the tooth crests, the air compressor Even if each tooth tip surface 29A, 36A expands toward the other end plate 28, 35 at the time of rated operation, the tooth tip surface 29A, 36A is expanded.
The sealing members 43, 44 fixed to the end plates 28, 35
It is possible to prevent the blades from being strongly pressed against and to be worn or damaged at an early stage, or to cause galling between the tooth top surfaces 29A and 36A.

Therefore, according to this embodiment, each wrap portion 2
9 and 36 tooth top surfaces 29A and 36A and the mating tooth bottom 28
A and 35A can be effectively sealed by the seal members 43 and 44, the compression efficiency can be surely increased, and the life of the seal members 43 and 44 can be extended to improve reliability. Can be made.

In the above embodiment, the case of using as a scroll type air compressor has been described as an example, but the present invention is not limited to this, and is used for, for example, a vacuum pump or a compressor for a cooling device. May be.

Further, in the above-mentioned embodiment, each concave groove 29B, 3
The width dimension of 6B is formed small on the inner peripheral side of each wrap portion 29, 36 and large on the outer peripheral side, and the inner peripheral portions 43A, 44A of the respective seal members 43, 44 are arranged on the inner peripheral side of the respective concave grooves 29B, 36B. Fitted and fixed, and the outer peripheral portion 4 of each seal member 43, 44
3B and 44B have been described as being loosely fitted to the outer peripheral sides of the recessed grooves 29B and 36B with a gap, but instead of this,
For example, the concave grooves 29B and 36B are formed with the same width dimension over the entire circumference, and the inner peripheral portion of about two turns is formed wide from the center side of each seal member 43 and 44, and the outer peripheral portion is formed more than this. The recesses 29B are formed to have a narrow width, and the inner peripheral portions of the seal members 43 and 44 are fitted and fixed to the inner peripheral sides of the recessed grooves 29B and 36B.
The outer peripheral portions of the seal members 43 and 44 may be loosely fitted on the outer peripheral sides of B and 36B.

Further, each of the seal members 43, 44 has an inner peripheral portion 43A, 44A, an outer peripheral portion 43A, 44B and a connecting portion 4.
Although it has been described as being constituted by the three parts 3C and 44C, instead of this, the respective sealing members 43 and 44 may be integrally formed of a single material.

[0049]

As described in detail above, according to the present invention, at least one of the wrap portions of the orbiting scroll and the fixed scroll is provided with an outer periphery of the wrap portion along the tooth top surface of the wrap portion. Side to inner peripheral side is formed, and a concave groove extending from the side to the inner peripheral side is formed. Inside the concave groove, the inner peripheral side of the lap portion is fixed to the concave groove, and the outer peripheral side of the lap portion floats inside the concave groove. Since the spiral seal member is provided, for example, when a gap is previously formed between the tooth top of the lap portion and the tooth bottom of the other side,
When the orbiting scroll starts an orbiting motion with respect to the fixed scroll, the seal member floats in the groove on the outer peripheral side of the wrap portion of the orbiting scroll or the fixed scroll and comes into slidable contact with the end plate (tooth root) of the other side, and the fluid Can be reliably contained at least in the compression chamber on the outer peripheral side, and the compression operation can be reliably performed. Then, since the lap portion on the inner peripheral side thermally expands due to the compression heat at this time, the dimension from the tooth bottom to the tooth tip is formed in advance in consideration of this thermal expansion amount, so that, for example, during the rated operation, The gap between the circumferential lap and the mating tooth bottom can be set to an appropriate size,
It is possible to prevent the seal member fixed to the lap portion on the inner peripheral side from being worn or damaged, prolonging the life of the seal member, improving the compression efficiency, and improving the reliability.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a scroll type air compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged view of a main part in FIG.

FIG. 3 is an enlarged front view showing a seal member.

FIG. 4 is a longitudinal sectional view of a main part of a scroll air compressor according to a conventional technique.

5 is a cross-sectional view showing an enlarged main part in FIG.

FIG. 6 is an exploded perspective view showing a wrap portion and a seal member of an orbiting scroll.

FIG. 7 is a characteristic diagram showing the relationship between the distance from the center of the wrap portion of the scroll type air compressor in the radial direction and the temperature of the wrap portion during rated operation.

[Explanation of symbols]

 21 casing 27 orbiting scroll 28 mirror plate 28A tooth bottom 29 wrap portion 29A tooth tip surface 29B concave groove 34 fixed scroll 35 end plate 35A tooth bottom 36 wrap portion 36A tooth tip surface 36B concave groove 43, 44 sealing member 43A inner peripheral portion 43B outer peripheral portion 43C connection

Claims (1)

[Claims] 1. A casing, an orbiting scroll rotatably provided in the casing, in which a spiral wrap portion is erected from a tooth bottom of an end plate, and fixed to the casing so as to face the orbiting scroll. A scroll-type fluid machine comprising: a fixed scroll in which a spiral wrap portion that overlaps with a wrap portion of an orbiting scroll to form a compression chamber is erected from a tooth bottom of an end plate. At least one of the lap portions is formed with a groove extending from the outer peripheral side to the inner peripheral side of the lap portion along the tooth crest surface of the lap portion, and the lap portion is provided in the concave groove. A scroll type fluid machine, characterized in that a spiral seal member is fixed to the concave groove on the inner peripheral side and floats in the concave groove on the outer peripheral side of the wrap portion.