JPH09250467A - Scroll type fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent leakage of pressure through the inside of a recess groove and improve compression performance by sealing an interval with the counterpart gear bottom face by means of a sealing member. SOLUTION: A backup seal 11 is arranged between the bottom face of a recess groove provided at each wrap part of a fixed scroll or a swivel scroll and each chip seal and is elastically pressurized by means of each backup seal 11 so that the chip seal always comes into slide contact with the gear bottom face. The backup seal 11 is provided with each protrusion 12 protruded from an inside face 11C, and a tip end 12A of each protrusion 12 elastically comes into contact with the side face of the recess groove.

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 Generally, a casing, a fixed scroll provided integrally with the casing and having a spiral wrap portion provided upright on the tooth bottom surface of an end plate, and a swivel in the casing facing the fixed scroll. And a revolving scroll in which a spiral wrap portion is erected so as to define a plurality of compression chambers on the tooth bottom surface of the end plate with the wrap portion of the fixed scroll, and is rotatable in the casing. And a drive shaft having a crank on the tip side connected to the orbiting scroll through an orbiting bearing, and at least one of the wrap portions of the fixed scroll and the orbiting scroll has the wrap portion. A scroll type fluid machine (hereinafter, referred to as a first type) in which a recessed groove extending along the tooth tip of
Of the prior art. ) Is known.

In such a scroll type fluid machine according to the first conventional technique, the base end side of the drive shaft projecting outside the casing is rotationally driven by a drive source such as a motor, and this rotation is cranked. To the orbiting scroll via an orbiting bearing, and the orbiting scroll is orbited about the drive shaft with a constant orbiting radius.

When used as a scroll type air compressor, for example, a plurality of compression chambers defined between the wrap portions of the fixed scroll and the orbiting scroll are continuously reduced by the orbiting motion of the orbiting scroll. While sequentially compressing the air sucked from the suction port in each compression chamber,
This compressed air is discharged from the discharge port toward an external air tank or the like.

In this case, a part of the compressed air enters from the compression chamber between the seal member and the groove formed in the tooth tip of the wrap portion, so that the pressure of the compressed air acts on the seal member. , The seal member is pressed toward the tooth bottom surface of the other party. As a result, the sealing member floats in the concave groove so as to come into sliding contact with the tooth bottom surface of the other side and performs a floating seal, and hermetically seals between the adjacent compression chambers via the lap portions.

Further, as a second conventional technique, for example, in the scroll compressors described in Japanese Utility Model Laid-Open No. 2-147887, Japanese Utility Model Laid-Open No. 2-147888 and Japanese Patent Laid-Open No. 3-11101, the side surface of the seal member is used. A plurality of notches are formed in the seal member and the bottom face side in the lengthwise direction of the seal member so that the side face and the bottom face side of the seal member are integrally formed with the plurality of side face lip parts and the plurality of bottom face side lip parts. I am trying to form.

Then, the side surface lip portion and the bottom surface side lip portion are elastically deformed by the pressure of the compressed air intruding into the groove, and the tip side thereof is brought into sliding contact with the side surface and the bottom surface side of the groove, respectively. As a result, the gap formed by communicating in the circumferential direction between the side surface and the bottom surface of the groove and the seal member is blocked,
The compressed air is prevented from leaking to the outer peripheral side from the high pressure side compression chamber to the low pressure side compression chamber through the gap.

On the other hand, as the third prior art, for example, Japanese Utility Model Laid-Open No. 59-117894 and Japanese Patent Laid-Open No. 60-24330.
In Japanese Patent Publication No. 1 and Japanese Patent Publication No. 63-54881, etc.,
An elastic member having a circular, annular or substantially V-shaped cross section is arranged between the bottom surface of the groove and the seal member, and the seal member is pressed against the tooth bottom surface of the other side.

[0009]

In the scroll type air compressor according to the first prior art described above, the pressure of the compressed air that has entered the groove from each compression chamber is utilized to move the seal member in the groove. Since only the so-called floating seal is carried out by floating, a gap is formed between the side surface of the concave groove, the bottom surface side and the seal member when the seal member floats toward the tooth bottom surface of the other party. Will end up. And
Since this gap communicates with the entire circumference in the spiral direction (circumferential direction) from the inner peripheral side to the outer peripheral side of the wrap portion in the concave groove, it is directed from the high pressure side compression chamber to the low pressure side compression chamber. There is a problem that compressed air leaks to the outer peripheral side through the gap, and the compression performance (compression efficiency) is reduced.

Further, in the second prior art, the side surface and the bottom surface side of the sealing member made of an elastic resin material are cut at regular intervals so that the side surface of the sealing member is formed over the entire length of the sealing member. Since a plurality of side surface lip portions and a plurality of bottom surface side lip portions are formed on the bottom surface side and the tip end side of each lip portion is opened by processing, the following problems occur.

That is, when the seal member is inserted into the groove formed in the tooth tip of the lap portion, the side surface lip portions are brought into contact with the side surface of the groove portion so as to bulge and slide (friction) between them.
Since the resistance increases, the pressure of the compressed air that has entered the groove from each compression chamber is used to float the seal member in the groove, and the seal member causes a gap between the tooth surface and the tooth surface of the other party. When attempting to seal, it is difficult to float the seal member in the groove on the outer peripheral side of the wrap where the pressure difference between the compression chambers is small, and the outer peripheral compression chambers are not necessarily airtight. There is a problem that can not be sealed.

Further, when the width of the seal member is made smaller than that of the groove or the width of the groove is widened so as to eliminate the protrusion of the side lip portions, the side surface of the groove and the seal are sealed. The gap between the members becomes large, the sealing action of each side lip is lost, and compressed air leaks from the high-pressure side compression chamber toward the low-pressure side compression chamber to the outer peripheral side through this gap. There's a problem.

Further, the seal member requires post-processing for making notches for forming the side surface lip portion and the bottom surface side lip portion, which increases man-hours required for manufacturing the seal member, resulting in poor workability. There is a problem of increasing costs. Further, in order to improve the sealing performance by the side surface lip portion and the bottom surface side lip portion, it is necessary to form the sealing member with a soft resin material, which is a hard material or any resin having wear resistance at high temperature. There is a problem that the material cannot be used and the selection range of the material is limited.

On the other hand, in the third conventional technique, an elastic member is used to elastically press the seal member from the groove toward the tooth bottom surface of the other party so that the seal member slides on the tooth bottom surface of the other party. It is designed to improve the sealing property.

However, since the elastic member has a circular, circular or substantially V-shaped cross section, when the elastic member is mounted in the U-shaped concave groove together with the seal member having a quadrangular cross section, the groove and the elastic member are separated from each other. A gap is generated between the compressed air and the compressed air leaks to the outer peripheral side through the gap to reduce the compression efficiency, and the temperature of the wrap portion, the seal member, the elastic member, and the like rises, and the durability decreases. was there.

The present invention has been made in view of the above-mentioned problems of the prior art, and it is possible to effectively seal the gap between the mating tooth bottom surface by the seal member and prevent the pressure from leaking through the concave groove. It is an object of the present invention to provide a scroll type fluid machine capable of improving compression performance.

[0017]

In order to solve the above problems, the present invention provides a fixed scroll in which a spiral wrap portion is erected on the tooth bottom surface of the end plate, and an end plate provided opposite to the fixed scroll. The present invention is applied to a scroll fluid machine including a revolving scroll in which a spiral wrap portion is erected so as to define a plurality of compression chambers on the tooth bottom surface of the fixed scroll.

The feature of the configuration adopted by the invention of claim 1 is that at least one of the wrap portions of the orbiting scroll and the fixed scroll is provided with a groove extending along the addendum of the wrap portion. A first seal member that is formed in the groove and is in sliding contact with the tooth bottom surface of the other party; and the first seal member that is arranged between the first seal member and the bottom surface of the groove. A second seal member that elastically presses from the groove toward the mating tooth bottom surface is provided, and the second seal member and one side surface of the groove are provided with the second seal member.
There is provided a plurality of elastic members which are spaced from each other in the length direction of the sealing member and elastically contact each other.

With this structure, the first seal member can be elastically pressed by the second seal member from the groove toward the mating tooth bottom surface, and the first seal member can be pressed against the mating tooth bottom surface. Between the side surface of the concave groove and the side surface of the concave groove by a plurality of elastic members elastically abutting between the second seal member and one of the side surfaces of the concave groove.
It is possible to surely seal the gap with the seal member.

According to the second aspect of the invention, the elastic member is a protrusion formed on the second seal member.

With this structure, the first seal member can be elastically pressed by the second seal member from the groove toward the mating tooth bottom surface, and the first seal member can be pressed against the mating tooth bottom surface. It is possible to reliably seal the gap between the second seal member and the side face of the concave groove and the second seal member by the protrusion of the second seal member.

According to the third aspect of the present invention, the second seal member is separated from the second seal member in the lengthwise direction so as to be flexibly curved along the side surface of the groove. To form a plurality of recesses.

With this structure, it is possible to suppress the deformation of the second seal member when it is mounted in the groove, and it is possible to improve the flexibility of the second seal member.

[0024]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

1 to 8 show a first embodiment of the present invention, and a scroll type air compressor will be described as an example of a scroll type fluid machine.

In the figure, reference numeral 1 denotes a casing of a scroll type air compressor formed in a stepped cylinder shape. The casing 1 has a large-diameter cylindrical portion 1A and a radial direction inside from one end side of the cylindrical portion 1A. An annular portion 1B extending in the direction, and a bearing tubular portion 1C extending in the axial direction so as to project from the inner peripheral side of the annular portion 1B toward the side opposite to the tubular portion 1A. Part 1
At the outer peripheral side portion of B, for example, three mounting portions 1D, 1D, ... (Only one is shown) are formed at predetermined intervals in the circumferential direction for mounting auxiliary cranks 26 described later.

Reference numeral 2 denotes a drive shaft rotatably provided in the bearing tubular portion 1C of the casing 1 via the bearings 3 and 3. The tip end side of the drive shaft 2 extends into the tubular portion 1A of the casing 1. The crank 2A becomes a crank 2A, and the axis of the crank 2A is eccentric with respect to the axis of the drive shaft 2 by a predetermined dimension. The drive shaft 2 projects from one end side of the bearing tubular portion 1C into a fan casing 30 described below, and a pulley 32 described below is provided on the projecting end side.

Reference numeral 4 denotes a fixed scroll fixed to the cylindrical portion 1A of the casing 1, and the fixed scroll 4 has a disk-shaped end plate 5 arranged so that its center coincides with the axis of the drive shaft 2. The spiral wrap portion 6 is axially erected from the tooth bottom surface 5A of the end plate 5, the center side is the winding start end and the outer peripheral side is the winding end end, and the wrap portion 6 is the outer circumference. The outer peripheral portion 7 is integrally formed on the outer side in the radial direction of the end plate 5 so as to surround it from the side and is attached to the cylindrical portion 1A of the casing 1 via a bolt (not shown) or the like. A large number of heat radiation fins 8, 8, ... Are formed on the back side of the end plate 5 located on the opposite side. The tip 6A of the wrap portion 6 is separated from the bottom surface 16A of the orbiting scroll 13 described below with a minute clearance C, as shown in FIG.

The radiating fins 8 extend in parallel with each other along the rear surface of the end plate 5 and form cooling air passages with the duct cover 33 described later. Then, in each of the heat radiation fins 8, the cooling air generated by the centrifugal fan 31 described later circulates linearly in each of the cooling air passages, so that the end plate 5 is formed.
The fixed scroll 4 is entirely cooled by radiating later-described compression heat or the like from the back side of the fixed scroll 4.

Reference numeral 9 denotes a concave groove formed on the tooth tip 6A side of the lap portion 6, and the concave groove 9 is located in the widthwise intermediate portion of the lap portion 6 and has a substantially horizontal cross section as shown in FIG. It is formed to have a letter shape. The groove 9 is composed of a bottom surface 9A, a side surface 9B located radially inside the wrap portion 6 and a side surface 9C located radially outside the wrap portion 6, and the groove 9 follows the spiral shape of the wrap portion 6. It extends from the winding start end to the winding end end. Further, the side surfaces 9B and 9C of the concave groove 9 are separated from each other with a width dimension W1, and the bottom surface 9A of the concave groove 9 and the tooth bottom surface 16A of the orbiting scroll 13 are opposed to each other with a predetermined separation dimension L. Then, a chip seal 10 and a backup seal 11 which will be described later are mounted in the concave groove 9 so as to seal between the bottom surface 16A of the orbiting scroll 13 which is a counterpart.

Reference numeral 10 denotes a tip seal as a first seal member mounted in the groove 9 of the wrap portion 6. The tip seal 10 is made of an elastic resin material excellent in wear resistance and slidability, such as poly Fluorine-based resin such as tetrafluoroethylene (PTFE), polyether sulfan (PES),
Polyphenylene sulfide (PPS), polyether ether ketone (PEEK), liquid crystal polymer (LCP)
Alternatively, it is formed in a long string shape using polysulfone (PSF) or the like, and extends spirally along the longitudinal direction of the groove 9.

The tip seal 10 is in contact with a sliding contact surface 10A which is in sliding contact with the tooth bottom surface 16A of the orbiting scroll 13 and an abutting surface 11A of a backup member 11 which is located on the opposite side of the sliding contact surface 10A. Mating surface 10B and concave groove 9
Inner side surface 10C facing the side surface 9B of the
Is formed on the opposite side to the side surface 9C of the concave groove 9 and the outer side surface 10D facing the side surface 9C so that the cross section has a substantially square shape.

The tip seal 10 has an inner surface 10C,
As shown in FIGS. 3 and 4, the width dimension W2 between the outer side surfaces 10D is formed to be smaller than the width dimension W1 of the concave groove 9, and the chip seal 10 has the sliding surface 10A and the abutting surface 10B. Is formed so that the height dimension is between T1 and T1. During the compression operation, the inner surface 10C of the tip seal 10 faces the high pressure side compression chamber 21 of each compression chamber 21, and the outer side surface 10D faces the low pressure side compression chamber 21.

Reference numeral 11 denotes the bottom surface 9A of the groove 9 and the tip seal 1.
0 shows a backup seal as a second seal member disposed between the backup seal 11 and the 0, and the backup seal 11 is, for example, a fluororesin such as polytetrafluoroethylene (PTFE), polyether sulfane (PES), polyphenylene. Of elastic resin materials such as sulfide (PPS), polyether ether ketone (PEEK), liquid crystal polymer (LCP) or polysulfone (PSF), elastic resin material softer than the tip seal 10 is formed into a long string shape. Thus, the spiral groove 9 extends along the longitudinal direction of the groove 9.

The backup seal 11 has an abutment surface 11A that abuts the abutment surface 10B of the tip seal 10.
An abutting surface 11B located on the opposite side of the abutting surface 11A and in contact with the bottom surface 9A of the concave groove 9, an inner side surface 11C facing the side surface 9B of the concave groove 9, and an opposite side of the inner side surface 11C. The lateral surface 9C of the concave groove 9 and the outer surface 11D facing the lateral groove 9 are formed to have a substantially quadrangular cross section, and a plurality of projections 12, 12, ...

The backup seal 11 has an inner surface 1
1C, the width W3 between the outer side surfaces 11D is smaller than the width W1 of the concave groove 9 as shown in FIGS.
W1), the width dimension W4 of the entire backup seal 11 including the projections 12 is formed to be slightly larger than the width dimension W1 of the concave groove 9 (W4> W1). further,
The backup seal 11 has an abutting surface 11A and an abutting surface 11B.
Is formed such that the height dimension is T2 between the tip seal 10 and the backup seal 11
The height dimension T2 of the groove 9 is slightly larger than the distance L between the bottom surface 9A of the groove 9 and the tooth bottom surface 16A of the orbiting scroll 13 (T1 + T2> L).

As shown in FIG. 6, reference numerals 12, 12, ... Denote projections formed on the inner surface 11C of the backup seal 11 with a projection dimension h, and each projection 12 is linear in the height direction of the backup seal 11. Extending to the tip 12
A has a semicircular shape and is formed at a predetermined interval along the length direction of the backup seal 11.
When the backup seal 11 is mounted in the groove 9, as shown in FIG. 7, each projection 12 has a tip 12A.
Elastically abuts the side surface 9B of the concave groove 9, and a small gap is formed between the side surfaces 9B of the concave groove 9 and the inner side surface 11C of the backup seal 11 between the protrusions 12.

Here, in a state where the tip seal 10 and the backup seal 11 are mounted in the concave groove 9 on the fixed scroll 4 side, the backup seal 11 has a groove width W4 including the protrusion 12 as shown in FIG. Since the width of the backup seal 11 is larger than the width W1 of W9 (W4> W1), the backup seal 11 is elastically deformed so that the central portion in the width direction rises in a convex shape.

When the wrap portion 6 of the fixed scroll 4 is disposed so as to face the tooth bottom surface 16A of the orbiting scroll 13, the sliding contact surface 10A of the tip seal 10 contacts the tooth bottom surface 16A on the orbiting scroll 13 side, The seal 10 presses the backup seal 11 into the concave groove 9. Furthermore, during operation of the scroll air compressor,
A thrust force acts on the orbiting scroll 13 in the thrust direction,
The orbiting scroll 13 presses the tip seal 10 further toward the backup seal 11 side, so the tip seal 10
The backup seal 11 made of a softer material has a shape as shown in FIG.

Reference numeral 13 denotes an orbiting scroll which is disposed so as to be capable of orbiting in the cylindrical portion 1A of the casing 1 so as to face the fixed scroll 4, and the orbiting scroll 13 includes an orbiting scroll body 14 and an orbiting scroll body 14. The orbiting scroll body 14 is composed of a fixed back plate 15, and the orbiting scroll body 14 is composed of an end plate 16, a spiral wrap portion 17 and the like, which are similar to those of the fixed scroll 4.

Here, the back plate 15 is a mirror plate 16
A boss portion 15A for holding a later-described swivel bearing 20 is integrally formed on the back surface side of the shaft through a bolt or the like. Further, on the outer peripheral side portion of the back plate 15, the mounting portions 15B, 15B, ... (1) for the auxiliary crank 26 are provided at positions substantially facing the respective mounting portions 1D on the casing 1 side.
(Only one is shown) are formed at a predetermined interval in the circumferential direction. Then, from the tooth bottom surface 16A of the end plate 16 to the lap portion 1
7 is erected in the axial direction, and the tooth top 17A of the wrap portion 17 is provided.
Are separated from the tooth bottom surface 5A of the fixed scroll 4 with a minute clearance C.

Further, as shown in FIG. 3, the tooth tops 17A of the wrap portion 17 also have the tooth tops 6 of the wrap portion 6 of the fixed scroll 4 as shown in FIG.
Similar to A, a concave groove 18 having a U-shaped cross section is formed from the bottom surface 18A and the side surfaces 18B and 18C. And
The tip seal 10 is mounted in the groove 18 in the same manner as the groove 9 on the fixed scroll 4 side.
The backup seal 11 is disposed between 0 and the bottom surface 18A of the concave groove 18.

.. are orbiting scroll main bodies 14
Radiating fins provided between the end plate 16 and the back plate 15 of the above, each radiating fin 19 is arranged on the back side of the end plate 16 so as to form a cooling air passage consisting of a linear concave groove, They run parallel to each other. Then, the cooling fins from the centrifugal fan 31 circulate in the cooling air passages in each of the radiating fins 19, thereby radiating the heat from the rear surface side of the end plate 16 and the boss portion 15A to cool them. There is.

Reference numeral 20 designates a slewing bearing inserted into the boss portion 15A of the back plate 15, and the crank 2A of the drive shaft 2 is attached to the inner peripheral side of the slewing bearing 20, and the crank 2A of the drive shaft 2 is attached. On the other hand, the orbiting scroll 13 is rotatably supported.

Reference numerals 21, 21, ... Denote a plurality of compression chambers defined between the wrap portion 6 of the fixed scroll 4 and the wrap portion 17 of the orbiting scroll 13, and each compression chamber 21 has a substantially crescent shape. When the orbiting scroll 13 orbits, the air between the suction ports 22 and 23 described later is gradually compressed and continuously discharged from the discharge port 25 described below by continuously contracting between the wrap portions 6 and 17. The wrap portion 17 of the orbiting scroll 13 is the fixed scroll 4
It is arranged so as to overlap with the lap portion 6 by a predetermined angle (for example, 180 degrees).

Reference numerals 22 and 23 denote outer edge portions 7 of the fixed scroll 4.
2 shows the first and second suction ports formed on the outer side of the end plate 5. The suction ports 22 and 23 are located on the outer side in the radial direction of the end plate 5 and sandwich the cooling air passages of the radiating fins 8 from above and below as shown in FIG. Thus, the end plates 5 are arranged so as to be separated from each other in the circumferential direction. The suction ports 22 and 23 communicate with the outermost peripheral compression chambers 21 of the compression chambers 21 and suck the outside air (suction air) into the compression chambers 21 via the suction filters 24. ing.

Reference numeral 25 denotes a discharge port provided on the center side of the end plate 5 of the fixed scroll 4, and the discharge port 25 is provided in each compression chamber 21.
The innermost peripheral (center) side of the compression chamber 21 is communicated with, and an air pipe (not shown) is connected to an external air tank.
And the like. Then, during operation of the scroll type air compressor, the air sucked from the suction ports 22 and 23 in accordance with the orbiting movement of the orbiting scroll 13 is sequentially compressed in each compression chamber 21, and finally the compression chamber 21 on the center side is compressed. The compressed air is discharged to the outside through the discharge port 25.

26, 26, ... Are annular parts 1 of the casing 1.
B is an auxiliary crank (only one is shown) as a rotation preventing mechanism which is disposed at a predetermined interval in the circumferential direction between B and the back plate 15 of the orbiting scroll 13, and each auxiliary crank 26 has one end on the casing 1 side. Is rotatably supported in each mounting portion 1D via a bearing 27, and the other end is rotatably supported in each mounting portion 15B of the back plate 15 via a bearing 28. Each of the auxiliary cranks 26 is eccentrically formed by a predetermined dimension like the crank 2A of the drive shaft 2, and is configured to prevent the orbiting scroll 13 from rotating when the orbiting scroll 13 orbits.

Reference numeral 29 denotes a balance weight that is fixed between the annular portion 1B of the casing 1 and the boss portion 15A of the back plate 15 and is fixed to the drive shaft 2. The balance weight 29 is used for the orbiting movement of the orbiting scroll 13. On the other hand, it balances the rotation of the entire drive shaft 2.

Reference numeral 30 denotes a fan casing attached to one end side of the bearing tube portion 1C of the casing 1. The fan casing 30 has a substantially spiral shape, and the inner peripheral side thereof serves as a cooling air intake 30A. It is open. Further, the outer peripheral side of the fan casing 30 communicates with a cooling air duct (not shown), and this cooling air duct extends toward the fixed scroll 4 side from the outer side of the casing 1. The cooling air duct is configured to allow the cooling air from the centrifugal fan 31 to flow into the cooling air passages on the orbiting scroll 13 side and the cooling air passages on the fixed scroll 4 side.

Reference numeral 31 denotes a centrifugal fan located inside the fan casing 30 and fixed to the projecting end side of the drive shaft 2 via a pulley 32. The centrifugal fan 31 rotates together with the drive shaft 2 to generate a fan. Cooling air is generated so that the outside air is taken into the casing 30, and this cooling air is forced to flow into the cooling air duct.
Further, the pulley 32 is connected to an electric motor serving as a drive source via a belt (neither is shown) or the like, and transmits the rotational force from the electric motor to the drive shaft 2 and also applies the rotational force to the centrifugal fan 31. It is configured to convey.

Further, numeral 33 indicates a duct cover arranged on the back side of the fixed scroll 4, and the duct cover 33 is fixed to the fixed scroll 4 so as to cover the tip side of each heat radiation fin 8 on the back side of the end plate 5. The cooling air passages are formed between the cooling air passages and the radiation fins 8. A pipe insertion hole 33A is formed in the center of the duct cover 33, and the air pipe connected to the discharge port 25 is inserted into the pipe insertion hole 33A.

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

First, when the drive shaft 2 is rotationally driven by the electric motor via the pulley 32, the rotation of the drive shaft 2 is transmitted from the crank 2A to the orbiting scroll 13 via the orbiting bearing 20, and the orbiting scroll 13 is rotated. The respective auxiliary cranks 26 rotate about the axis of the drive shaft 2 while preventing rotation. The compression chambers 21, 21, ... Defined between the wrap portions 6, 17 are continuously contracted by this swiveling motion, whereby the scroll air compressor sucks in from the suction ports 22, 23. The compressed air is sequentially compressed in each compression chamber 21, and the compressed air is discharged from the discharge port 25 to an external air tank (not shown) or the like.

However, in this embodiment, each wrap portion 6, 1
A backup seal 11 is provided between the bottom surfaces 9A and 18A of the concave grooves 9 and 18 of FIG. 7 and the respective tip seals 10, and the tip seals 10 are pushed up by the respective backup seals 11 toward the tooth bottom surfaces 16A and 5A of the other party. Since the sliding contact surface 10A of the tip seal 10 is elastically pressed so as to be constantly in sliding contact with the tooth bottom surfaces 16A and 5A, the compressed air is high in pressure between the tip seal 10 and the tooth bottom surfaces 16A and 5A. It is possible to reliably prevent leakage from the compression chamber 21 on the low pressure side to the compression chamber 21 on the low pressure side.

Since the tip seal 10 is constantly brought into sliding contact with the mating tooth bottom surfaces 16A and 5A by the backup seal 11, it is not necessary to float the tip seal 10 in the concave grooves 9 and 18 by utilizing the pressure of compressed air. Also, the tip seal 10 can be surely attached to the tooth bottom surfaces 16A, 5 of the other side even on the outer peripheral side of the lap portions 6, 17 where the differential pressure between the compression chambers 21 is small.
A can be contacted with A, and uniform sealability can be secured over the entire length of the tip seal 10.

On the other hand, the backup seal 11 is provided with each protrusion 12 projecting from the inner surface 11C.
Since the tip 12A of the second member elastically abuts the side surfaces 9B and 18B of the recessed grooves 9 and 18, the protrusion 12 seals between the inner side surface 11C of the backup seal 11 and the side surfaces 9B and 18B of the recessed grooves 9 and 18. Therefore, it is possible to reliably prevent the compressed air from leaking from the high pressure side to the low pressure side compression chamber 21 along the concave grooves 9 and 18, and to improve the compression efficiency.

In addition, the tip seal 10 is provided in the concave grooves 9 and 18.
And the backup seal 11 are abutting surfaces 10B and 11A.
Abut with, and tip seal 10 and backup seal 1
Since a gap is not formed between the wrap portions 1 and 1, it is possible to prevent the temperature of the lap portions 6 and 17, the tip seal 10, the backup seal 11 and the like from rising due to the recompression of the air that has entered this gap, and improve the durability.

The backup seal 11 as the second seal member has the protrusions 12 on the inner surface 11C,
Since the protrusions 12 can be integrally formed when the backup seal 11 is formed, it is not necessary to form the lip portion and the like by special post-processing as in the second conventional technique, and workability during production can be improved. . The tip seal 10 that is in sliding contact with the tooth bottom surface 16A of the other side is not required to have high dimensional accuracy in accordance with the concave grooves 9 and 18 as in the prior art, and the tip seal 10 is not provided with a lip portion or the like. Since it is not necessary to form the tip seal 10 using a soft resin material, the tip seal 10 can be easily manufactured, the selection range of materials can be widened, and the tip seal 10 has a hard material and wear resistance at high temperature. Materials can be used.

Further, since the tip seal 10 can be made of a resin material having excellent wear resistance and the backup seal 11 can be made of a resin material having a high elasticity, the tip seal 10 can be made of a mating tooth. Bottom 16
While ensuring the sealing performance with A and 5A, the backup seal 11 uses the tip seal 10 as the mating tooth bottom surface 16A,
5A can be pressed, and the insides of the concave grooves 9 and 18 can be reliably sealed through the respective projections 12, and the slidability of the tip seal 10 can be improved.
Reliability can be improved and life can be extended.

Thus, according to this embodiment, the concave grooves 9, 1
By the backup seal 11 arranged between the bottom surfaces 9A and 18A of 8 and the tip seal 10, the tip seal 10 can be installed even in a place where the pressure of the compressed air is relatively low such as the outer peripheral side of the fixed scroll 4 and the orbiting scroll 13. The tip seal can be surely pressed toward the tooth bottom surfaces 16A, 5A of the other party, and the tip seal 10 can be pressed against the tooth bottom surfaces 16A, 5A of the other party.
It is possible to make a stable sliding contact at all times.

Further, the tips 12A of the respective projections 12 provided on the backup seal 11 have side surfaces 9B and 18 of the concave grooves 9 and 18, respectively.
Since it elastically abuts on B, it is possible to prevent compressed air from leaking to the compression chamber 21 on the low pressure side through the concave grooves 9 and 18.
The compression performance can be significantly improved.

Next, FIG. 9 shows a second embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof is omitted. To However, the feature of this embodiment is that the projection 42 is provided on the inner surface 41C of the backup seal 41 as the second seal member, and the backup seal 41 is flexibly curved along the outer surface 41D in the longitudinal direction. This is because the semicircular notch 43, which is a plurality of recesses and is separated from each other, is provided.

Here, the backup seal 41 has an abutment surface 41A, an abutment surface 41B, an inner side surface 41C and an outer side surface 41D, which is similar to the backup seal 11 described in the first embodiment. The mating surface 41A and the contact surface 41B are opposed to each other with a height dimension T2, and the inner surface 41C and the outer surface 41D are opposed to each other with a width dimension W3. Further, from the inner surface 41C of the backup seal 41, the tip 42
A projections 42 each having a semicircular shape are provided with a projection dimension h, and the sum of the projection dimension h of each projection 42 and the width dimension W3 between the inner surface 41C and the outer surface 41D is a width dimension W4.

The outer surface 41D is provided with semicircular cutouts 43, 43, ... At positions corresponding to the protrusions 42, and the cutouts 43 extend linearly in the height direction of the cutout 43. However, the backup seal 41 is formed at a predetermined interval along the length direction.

Thus, in this embodiment having such a structure, it is possible to obtain substantially the same operation and effect as in the first embodiment. However, particularly in this embodiment, the notch is formed in the outer surface 41D of the backup seal 41. Since the portion 43 is provided, the central portion in the width direction when the backup seal 41 is mounted in the recessed grooves 9 and 18 rises like the backup seal 11 (see FIG. 8) described in the first embodiment. Instead, the backup seal 41 can be flexibly curved along the spiral of the wrap portions 6 and 16, and the backup seal 41 can be easily attached.

Next, FIGS. 10 and 11 show the third embodiment of the present invention.
In the present embodiment, the same components as those in the first embodiment will be designated by the same reference numerals, and the description thereof will be omitted. However, the feature of this embodiment is that the flat plate-like projection 5 that can be expanded on the inner surface 51C of the backup seal 51 is used.
2, 52, ... are provided.

Here, the backup seal 51 includes an abutting surface 51A, an abutting surface 51B, an inner side surface 51C and an outer side surface 51.
D has a height dimension T between the abutting surface 51A and the abutting surface 51B.
2, and the inner surface 51C and the outer surface 51D are opposed to each other with a width W5. Further, each projection 52 projecting at an inclination angle θ is integrally formed from the inner surface 51C of the backup seal 51, and the tip 5 of each projection 52 is formed.
The distance between 2A and the outer side surface 51D has a width W4.

When the backup seal 51 is mounted in the recessed grooves 9 and 18, the tips 52A of the protrusions 52 are curved toward the inner surface 51C, as shown in FIG. Here, a part of the compressed air enters the concave grooves 9 and 18 by the compression operation, and the pressure of the compressed air is applied in the E direction indicated by the arrow, whereby the projections 52 expand in the E direction indicated by the arrow. The tip 52A comes into elastic contact with the side surfaces 9C and 18C of the concave grooves 9 and 18.

Further, the backup seal 51 is formed by each projection 5
Since there is a recess between the two and the width W5 of the recess is reduced, the backup seal 51
Can be given flexibility, and the backup seal 51 can be smoothly curved along the concave grooves 9 and 18.

Thus, in this embodiment having the above-described structure, substantially the same operation and effect as those of the first embodiment can be obtained, but in this embodiment, the backup seal 51 projects at an inclination angle θ that can be expanded. Since each protrusion 52 is provided,
The tips 52A of the respective projections 52 can be elastically brought into contact with the side surfaces 9C and 18C of the concave grooves 9 and 18 by the pressure of compressed air, and the compressed air on the low pressure side is transmitted through the concave grooves 9 and 18. Leakage into the chamber 21 can be reliably prevented.

Next, FIG. 12 shows a fourth embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. To However, the feature of this embodiment is that the backup seal 61 has an outer portion 61A having a height dimension T2 so that the cross section has an L shape, and an inner portion 61B having a height dimension T3 (T3 <T2). Is formed into a stepped string shape, and the backup seal 61 is provided with a plurality of substantially flat plate-like projections 62, 62 having a height dimension T2 from the outer portion 61A to the inner portion 61B.
It is provided to project to the side.

Here, the outer side portion 61A of the backup seal 61 has a width dimension W6, and the inner side portion 61B has a width dimension W7.
Having. Then, the outer surface 6 of the backup seal 61
The distance between 1C and the tip 62A of each protrusion 62 is a width dimension W4, which is greater than the total width dimension (W6 + W7) of the outer portion 61A and the inner portion 61B (W6 + W7).
7 <W4) is formed.

Thus, in this embodiment having such a structure, substantially the same operation and effect as in the first embodiment can be obtained. However, in this embodiment, the tips 62A of the projections 62 are formed into the concave grooves 9 and 18. The side surfaces 9C and 18C can be elastically contacted, and the backup seal 61 and the recessed grooves 9 and 18 can be more reliably sealed.

In each of the above-mentioned embodiments, the tip seal 10 and the backup seal 11 are mounted in the concave groove 9 on the fixed scroll 4 side and the concave groove 18 on the orbiting scroll 13 side. Not limited to this, a groove is formed in the wrap portion on either the fixed scroll 4 side or the orbiting scroll 13 side, and the tip seal and the backup seal as the first and second seal members are mounted in the groove. It may be configured to.

Further, in each of the above-described embodiments, the scroll type air compressor has been described as an example of the scroll fluid machine, but it can be widely applied to, for example, a vacuum pump, a refrigerant compressor and the like.

Further, in each of the above-mentioned embodiments, the projections 12, 4
Reference numerals 2, 52 and 62 constitute the elastic member according to the present invention, and the elastic member may be provided on one side surface of both side surfaces of the concave groove.

[0078]

As described in detail above, according to the first aspect of the invention, the first and second seal members are arranged in the concave groove of the wrap portion, and the first seal is provided by the second seal member. The member is elastically pressed from the groove toward the tooth bottom surface of the other side, and the second seal member and one of the side surfaces of the groove are spaced apart from each other in the longitudinal direction of the second seal member. Since a plurality of elastic members that have elastic contact with each other are provided,
The first seal member can surely be brought into sliding contact with the tooth bottom surface of the other party, and pressure is applied from the high-pressure side compression chamber to the low-pressure side compression chamber through the space between the first seal member and the other tooth bottom surface. Can be surely prevented from leaking. And the first
Since the second sealing member constantly makes sliding contact with the tooth bottom surface of the other side, it is not necessary to levitate the first sealing member in the concave groove by utilizing the pressure of compressed air. Even on the outer peripheral side of the lap portion where the differential pressure is small, the first seal member can surely contact the tooth bottom surface of the other side, and uniform sealability can be secured over the entire length of the first seal member.

Further, since the elastic member elastically abutting is provided between the second seal member and one of the side surfaces of the concave groove, the gap between the second seal member and the side surface of the concave groove is provided. It is possible to seal, it is possible to reliably prevent the pressure from leaking to the low pressure side through the groove, and it is possible to improve the compression efficiency.

Furthermore, since a resin material having excellent wear resistance can be used for the first seal member and a resin material having a high elastic force can be used for the second seal member, The seal member secures the sealability with the tooth bottom surface of the other party, while the second seal member can press the first seal member toward the tooth bottom surface of the other party to surely seal the inside of the concave groove. The slidability and reliability of the seal member can be improved and the life can be extended.

On the other hand, in the invention described in claim 2, since the elastic member is the projection formed on the second seal member, each projection is elastically brought into contact with the side surface of the concave groove to form the second seal member. It is possible to seal between the side surface of the concave groove and surely prevent the pressure from leaking to the low pressure side through the concave groove and improving the compression efficiency. Further, the respective protrusions can be integrally formed at the time of molding the second seal member, and it is not necessary to form the lip portion and the like by special post-processing. Further, the first seal member that is in sliding contact with the tooth bottom surface of the other side does not require high dimensional accuracy in accordance with the concave groove as in the conventional technique,
Since it is not necessary to form the sealing member of the soft resin material, the first sealing member can be easily formed, the selection range of the material can be widened, and the hard material and the wear resistance at high temperature can be obtained. Can be used.

According to the third aspect of the present invention, the second seal member is separated from the second seal member in the lengthwise direction so that the second seal member is flexibly curved along the side surface of the groove. Since the plurality of recesses are formed, when the second seal member is mounted in the recess groove, it is possible to prevent the center portion of the second seal member in the width direction from being deformed so as to bulge. Can be flexibly curved along the spiral of the wrap portion, and the second seal member can be easily mounted in the groove.

[Brief description of the drawings]

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

FIG. 2 is an enlarged cross-sectional view of a main part showing an orbiting scroll, a fixed scroll, and the like as seen from the direction of arrows II-II in FIG.

FIG. 3 is a sectional view taken along the line III-III in FIG.

4 is a cross-sectional view of the tip seal shown in FIG.

5 is a cross-sectional view of the backup seal shown in FIG.

FIG. 6 is a partial perspective view of the backup seal shown in FIG.

7 is a sectional view taken along line VII-VII in FIG.

FIG. 8 is a sectional view showing a state in which the tip seal and the backup seal are mounted in the concave groove, as viewed from the same position as in FIG.

FIG. 9 is a partial perspective view of a backup seal used in a scroll air compressor according to a second embodiment of the present invention.

FIG. 10 is a partial perspective view of a backup seal used in a scroll air compressor according to a third embodiment of the present invention.

FIG. 11 is a sectional view showing a backup seal used in a scroll type air compressor according to a third embodiment of the present invention, as seen from the same position as in FIG. 7.

FIG. 12 is a partial perspective view showing a backup seal used in a scroll air compressor according to a fourth embodiment of the present invention.

[Explanation of symbols]

1 Casing 2 Drive shaft 2A Crank 4 Fixed scroll 5,16 End plate 5A, 16A Tooth bottom face 6,17 Lap part 6B, 17A Tooth tip 9,18 Recessed groove 9A, 18A Bottom face 9B, 9B, 18B, 18C Side face 10 Chip seal ( First seal member) 11, 41, 51, 61 Backup seal (second seal member) 12, 42, 52, 62 Protrusion (elastic member) 13 Orbiting scroll 14 Orbiting scroll body 15 Back plate 21 Compression chamber 43 Notch (Recess)

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroyuki Mihara 1-6-3 Fujimi, Kawasaki-ku, Kanagawa Prefecture Tokiko Corporation

Claims (3)

[Claims] 1. A fixed scroll in which a spiral wrap portion is erected on the tooth bottom surface of an end plate and a plurality of wrap portions of the fixed scroll provided on the end surface of the end plate of the end plate facing the fixed scroll. In a scroll type fluid machine comprising a revolving scroll in which a spiral wrap portion is erected so as to define a compression chamber, in at least one of the wrap portions of the revolving scroll and the fixed scroll. Forming a recessed groove extending along the tooth top of the wrap portion, and in the recessed groove, a first seal member that is in sliding contact with the tooth bottom surface of the other party, and a bottom surface of the first seal member and the recessed groove. And a second seal member which is disposed between the second seal member and the groove to elastically press the first seal member from the groove toward the tooth bottom surface of the other side. On one of the two side surfaces, the second Scroll fluid machine according to claim resiliently providing the plurality of elastic members abut therebetween have a gap in the length direction of the seal member. 2. The scroll fluid machine according to claim 1, wherein the elastic member is a projection formed on the second seal member. 3. The second seal member is formed with a plurality of recesses spaced apart in the longitudinal direction so that the second seal member flexibly curves along the side surface of the groove. The scroll fluid machine according to claim 1 or 2.