JP2006299986A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor having a reduced minimum refrigerant discharge amount while maintaining a minimum revolving speed. <P>SOLUTION: The scroll compressor 1 comprises a fixed scroll 19 having a fixed scroll spiral body 19b in a spiral shape erected on one side face of a fixed scroll end plate 19a, and a revolving scroll 21 having a revolving scroll spiral body 21b in a spiral body erected on one side face of a revolving scroll end plate 21a and supported in revolving motion with the revolving scroll spiral body 21b engaging with the fixed scroll spiral body 19b to form a compression chamber P. Between the front end of the fixed scroll spiral body 19b and the revolving scroll end plate 21a and between the revolving scroll spiral body 21b and the fixed scroll end plate 19a, enlarged parts 51, 55 are provided, respectively, which have a larger space at the winding end sides of the fixed scroll spiral body 19b and the rotary scroll spiral body 21b than at the center sides. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in a refrigerant compressor such as an air conditioner.

Piston type, rotary type, and scroll type compressors are known as refrigerant compressors for air conditioners. Among them, scroll compressors are widely used because they have the advantages of high efficiency, low noise, and low vibration compared to other systems.
The scroll compressor has a spiral wall on one side, a fixed scroll fixedly supported in a housing connected to the suction pipe and the discharge pipe, and a spiral wall provided on one side. The body is placed in mesh with the wall of the fixed scroll in the vertical or horizontal direction, and is prevented from rotating by the Oldham link mechanism. And orbiting scroll for performing.
In the scroll compressor, the wall of the orbiting scroll contacts the wall of the fixed scroll at a plurality of contact points to form a crescent-shaped compression chamber, and the compression chamber moves inward while reducing the volume from the outer peripheral side. Thus, suction, compression, and discharge can be performed simultaneously.

In air conditioners, diversification of operation modes is required, and accordingly, a scroll compressor is required to be operated at a variable speed by inverter control or the like.
Moreover, what is shown by patent document 1 is proposed as what can drive | operate efficiently over the wide range from low speed driving | operation to high speed driving | operation in such variable speed driving | operation.
This is because at least one of the fixed scroll and the orbiting scroll wall is provided with a spiral extension wall extending further from the winding end position, and at least one of the inner wall of the extension wall and the outer wall of the wall opposite thereto is provided. The scroll compressor can be operated efficiently over a wide range from a small capacity to a large capacity with a variable speed by displacing the wall in the direction of decreasing the wall thickness and increasing the mutual spacing. It is.

Japanese Patent No. 33999797

By the way, in the scroll compressor, since it is necessary to form an oil seal between the orbiting scroll and the fixed scroll, it is configured to maintain a certain rotational speed or more.
On the other hand, in the air conditioner, for example, when the amount of refrigerant required is small, such as during air conditioning in an intermediate period, there is a demand for reducing the discharge amount from the scroll compressor. For this reason, for example, in a particularly large air conditioner, a part of the refrigerant discharged from the scroll compressor is bypassed, and the refrigerant amount is adjusted not to be sent to the indoor unit.
The one disclosed in Patent Document 1 mainly increases the refrigerant discharge amount with respect to the rotation speed of the scroll compressor, and satisfies the requirement to reduce the minimum capacity (minimum refrigerant discharge amount) of the scroll compressor. It is not a thing. Furthermore, since the expanding interval is in the radial direction, the part inspection process is difficult.

  In view of the above problems, an object of the present invention is to provide a scroll compressor that can reduce a minimum refrigerant discharge amount while maintaining a minimum rotation speed and facilitates a component inspection process.

In order to solve the above problems, the present invention employs the following means.
That is, the scroll compressor according to the present invention includes a fixed scroll having a spiral fixed side wall standing on one side surface of a fixed side end plate, and a spiral shape standing on one side surface of a turning side end plate. A scroll compressor having a revolving side wall and a revolving scroll supported so as to be capable of revolving orbiting so as to form a compression chamber by engaging the revolving side wall and the fixed side wall. At least one of the front end portion of the swivel side end plate and the swivel side wall body and the fixed side end plate is spaced from the fixed side wall body or the winding end side of the swivel side wall body. Is provided with an enlarged portion formed larger than the center side.

The lubricating oil is carried to the compression chamber by the sucked refrigerant gas, and forms an oil seal between the fixed side end plate and the swiveling side wall body and between the swiveling side end plate and the fixed side wall body. This prevents seizure or the like in these portions and prevents the refrigerant gas from leaking.
At this time, the amount of lubricating oil carried to the compression chamber varies depending on the amount of refrigerant gas sucked, that is, the rotational speed, and there is a margin at high speed operation, but at low speed operation, it is rapidly reduced as the rotational speed decreases. become.
According to the present invention, at least one of the end of the fixed side wall and the swivel side end plate and between the swivel side wall and the fixed side end plate is the end of winding of the fixed side wall or the swivel side wall. Since there is an enlarged portion formed on the side with a larger interval than the center side, when the rotational speed decreases and the amount of lubricant to be carried becomes less than a predetermined amount, the oil seal is sufficiently secured except for the enlarged portion. Even if maintained, the oil seal in the enlarged portion is not sufficiently formed.
If the oil seal of the enlarged portion is not sufficiently formed, the refrigerant gas leaks from the enlarged portion, so that the amount of refrigerant gas sucked into the compression chamber is reduced. For this reason, the amount of refrigerant gas discharged from the compression chamber can be reduced.

Since the leakage of the refrigerant gas in the enlarged portion increases as the operation speed decreases, the amount of refrigerant gas discharged during low-speed operation can be further reduced as compared with the conventional case.
Thus, since the amount of refrigerant gas discharged at low speed operation can be reduced, for example, when the amount of refrigerant required is small, such as during air conditioning in the intermediate period, there is a possibility that only the scroll compressor can be used. . In this case, for example, it is not necessary to install equipment for bypassing excess refrigerant gas, so that the manufacturing cost of the air conditioner can be reduced.
In addition, it is preferable from the viewpoint of maintaining the compression efficiency that the interval in the enlarged portion is set to a size that can form an oil seal when there is a sufficient amount of lubricating oil carried in at high speed operation.

  In the scroll compressor according to the present invention, the enlarged portion is formed in a portion of the fixed side wall body or the turning side wall body that is less than one turn on the winding end side.

According to the present invention, since the enlarged portion is formed in a portion of the fixed side wall body or the swiveling side wall body that is less than one turn on the winding end side, the compression chamber formed on the outermost side is the winding end end of the wall body. Thus, the refrigerant gas will not leak after the suction is closed.
As described above, since the compressed refrigerant gas does not leak after the deadline, it is possible to prevent the power that compressed the refrigerant gas from being wasted.

  In the scroll compressor according to the present invention, the enlarged portion is formed so that the interval gradually increases toward the winding end side of the fixed side wall body or the turning side wall body.

In this way, since the enlarged portion is formed so that the interval gradually increases toward the winding end side of the fixed side wall body or the swiveling side wall body, it gradually increases from the winding end end side toward the inside as the rotational speed decreases. Insufficient oil seal. For this reason, since the portion where the refrigerant gas leaks gradually increases from a certain rotational speed as the rotational speed decreases, the amount of discharged refrigerant gas can be gradually reduced. Since the discharge refrigerant gas amount can be gradually reduced, the discharge refrigerant gas amount can be easily adjusted.
Moreover, since the leakage of the refrigerant gas proceeds from the winding end end side where the progress of compression is small, power loss can be reduced.

  In the scroll compressor according to the present invention, the enlarged portion is formed by lowering the height of the fixed side wall body or the turning side wall body.

  As described above, since the enlarged portion is formed by lowering the height of the fixed side wall body or the swivel side wall body, the processing range is narrower than that of the fixed side end plate or the swivel side end plate. Can do.

  According to the present invention, at least one of the end of the fixed side wall and the swivel side end plate and between the swivel side wall and the fixed side end plate is the end of winding of the fixed side wall or the swivel side wall. Since the enlarged portion is formed on the side having an interval larger than that of the center side, the minimum refrigerant discharge amount can be reduced while maintaining the minimum rotational speed at which an oil seal can be formed at a portion other than the enlarged portion.

Hereinafter, a scroll compressor according to an embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a longitudinal sectional view showing the overall structure of a scroll compressor 1 used in a refrigerant compressor of an air conditioner to which the present invention is applied.
The scroll compressor 1 includes a bottomed cylindrical housing 3 that extends vertically, a scroll compression mechanism 7 supported by an upper bearing 5 at an upper portion inside the housing 3, and a lower part of the scroll compression mechanism 7, that is, the housing 3. A motor 9 serving as driving means is disposed at the lower part of the inside and supported by the housing 3, and a drive shaft 11 of the motor 9 is coupled to the lower part of the scroll compression mechanism 7.

A discharge pipe 13 is provided through the top of the housing 3. A suction pipe 15 is provided on the outer periphery of the top of the housing 3 so as to penetrate the housing 3 and communicate with a suction chamber 17 described later.
The scroll compression mechanism 7 includes a fixed scroll 19 fixed to the upper bearing 5, a orbiting scroll 21 supported between the upper bearing 5 and the fixed scroll 19 via a thrust bearing so as to be capable of revolutionary orbiting, A well-known Oldham link mechanism 23 provided on the outer surface of the scroll 21 and preventing the rotation of the orbiting scroll 21 while allowing the orbiting of the orbiting scroll 21 is provided.

The fixed scroll 19 includes a fixed scroll end plate (fixed side end plate) 19a, a spiral fixed scroll spiral body (fixed side wall body) 19b erected downward on the inner surface of the fixed scroll end plate 19a, And a cylindrical peripheral wall portion 19c formed at the peripheral edge portion of the fixed scroll end plate 19a. A discharge valve 27 that opens and closes the discharge port of the discharge passage 25 and a discharge valve retainer 29 that restricts the movement of the discharge valve 27 are provided near the center of the fixed scroll end plate 19a.
The suction port provided at the lower end of the suction pipe 15 is connected to a suction chamber 17 formed between the fixed scroll 19 and the orbiting scroll 21. A suction flow path is formed.

  The orbiting scroll 21 is fixed upright on the inner surface of the orbiting scroll end plate 21a and the inner surface of the orbiting scroll end plate 21a. A spiral orbiting scroll spiral body (orbiting side wall body) 21b meshed with the scroll spiral body 19b is provided. A cylindrical boss 31 is erected on the lower surface of the orbiting scroll end plate 21a with the same axis center. A bush 33 is rotatably fitted inside the boss 31 via a swivel bearing 35.

The fixed scroll 19 and the orbiting scroll 21 are 180 degrees out of phase so that the side surfaces of the fixed scroll spiral body 19b and the orbiting scroll spiral body 21b are in line contact with each other at a plurality of positions in a state where they are eccentric from each other by a predetermined distance. Are engaged with each other.
In this state, the front end surface of the fixed scroll spiral body 19b and the front end surface of the orbiting scroll spiral body 21b have a predetermined distance D1 on the inner surfaces of the orbiting scroll end plate 21a and the fixed scroll end plate 19a, respectively. .
The fixed scroll spiral body 19b and the orbiting scroll spiral body 21b form compression chambers P serving as sealed spaces at a plurality of locations that are point-symmetric with respect to the center.
Note that the orbiting scroll 21 is arranged to be capable of revolving orbiting in a state where rotation is prevented with respect to the upper bearing 5 and the fixed scroll 19 fixed to the upper bearing 5 by the well-known Oldham link mechanism 11. .

Next, the enlarged portion of the present invention will be described with reference to FIGS.
FIG. 2 is a perspective view showing an overall schematic configuration of the orbiting scroll 21. FIG. 3 is a development view showing a state in which the orbiting scroll spiral body 21b is developed.
On the winding end end side of the orbiting scroll spiral body 21b, there is provided an orbiting side lower portion 49 having a lower tooth height than the central tooth height H1. The length L along the spiral curve of the swivel side lower portion 49 is provided over substantially a quarter of the circumference from the end of the winding.
Accordingly, most of the orbiting scroll spiral body 21b is spaced at the same interval as in the prior art.

The tooth height of the swivel side lower portion 49 is formed so as to gradually decrease substantially linearly from the center side tooth height H1 to the winding end end tooth height H2. For this reason, the space | interval of the rotation side low-order part 49 and the fixed side end plate 19a in this part is increasing gradually from the space | interval D1 of a center side to the space | interval D2 of a winding end, and the enlarged part 51 is formed. become.
In addition, the space | interval D2 is set to the magnitude | size in which an oil seal is fully formed at the time of high speed rotation.
In addition, on the winding end end side of the fixed scroll spiral body 19b, a fixed side lower portion 53 having the same configuration as that of the orbiting scroll spiral body 21b is provided, and an enlarged portion 55 is similarly formed. (See Figure 1)

Returning to FIG. 1, a back pressure chamber 37 is provided around the boss 31 between the orbiting scroll 21 and the upper bearing 5. The back pressure chamber 37 is maintained at a high pressure equivalent to the discharged gas during the operation of the scroll compressor 1. The high pressure presses the orbiting scroll 21 in the direction of the fixed scroll 19.
The drive shaft 11 of the motor 9 is pivotally supported by the upper bearing 5 and a lower bearing 39 positioned below the motor 9, and an eccentric pin 41 that is eccentric by a predetermined amount from the axis is provided in a protruding state at the upper end. The eccentric pin 41 is inserted into the through hole of the bush 33 and supports the bush 33 so as to be rotatable.
The eccentric pin 41 and the drive shaft 11 are formed with an oil passage 43 penetrating them vertically, and a lubricating oil pump mechanism 45 is provided at the lower end of the drive shaft 11. A lubricating oil 47 is stored at the bottom of the housing 3, and a lubricating oil pump mechanism 45 at the lower end of the drive shaft 11 is disposed in the lubricating oil 47.

The operation of the scroll compressor 1 according to the present embodiment described above will be described.
When the drive shaft 11 is rotated by the motor 9, the orbiting scroll 21 performs a revolving orbiting motion while being prevented from rotating by the Oldham link mechanism 23.
When the refrigerant gas is introduced into the suction chamber 17 through the suction pipe 15, the refrigerant gas is sucked into the compression chamber P formed by the fixed scroll spiral body 19b and the orbiting scroll spiral body 21b, and the compression chamber P sequentially moves inward. It is compressed by. The compressed high-pressure refrigerant gas is discharged through the discharge passage 25 by opening the discharge valve 27. The discharged high-pressure refrigerant gas is sent from the discharge pipe 13 to the heat exchanger of the air conditioner.
At this time, high-pressure refrigerant gas is also introduced into the back pressure chamber 37, and the back pressure chamber 37 becomes high pressure.

During the operation of the scroll compressor 1, the lubricating oil 47 stored in the lower portion of the housing 3 is supplied to the upper portion through the oil passage 43 provided in the drive shaft 11 by the lubricating oil pump mechanism 45 and is supplied to the back pressure chamber 37. Charged.
The filled lubricating oil maintains the high pressure of the back pressure chamber 37 and acts on the boss 31 and the orbiting scroll end plate 21a facing the back pressure chamber 37 of the orbiting scroll 21, thereby turning the orbiting scroll 21. Is pressed against the fixed scroll 19.
Further, a part of the lubricating oil 22 lubricates the portions of the slewing bearing 35, the bush 33 and the eccentric pin 41, and further lubricates the shaft support portion of the upper bearing 5.
The lubricating oil 47 that has lubricated these portions passes through the surface of the drive shaft 11 and is collected in the lower portion of the housing 3.

Further, the lubricating oil 47 in the back pressure chamber 37 is also supplied to the suction chamber 17. The lubricating oil 47 supplied to the suction chamber 17 is carried to the compression chamber P by the refrigerant gas flowing into the suction chamber 17 from the suction pipe 15 and lubricates the engaging portion between the fixed scroll 19 and the orbiting scroll 21. Become. As a result, an oil seal is formed in the space D1 provided between the turning of the fixed scroll end plate 19a and the scroll spiral body 21b and between the turning scroll end plate 21a and the fixed scroll spiral body 19b.
Also, the lubricating oil 47 sent to the compression chamber P cools the motor in the housing, and is then discharged from the discharge pipe 13 together with a part of the refrigerant gas, circulates through the air conditioner and passes through the suction pipe 15. It will be returned to the suction chamber 17.
Further, the lubricating oil 47 recovered between the discharge passage 25 and the discharge pipe 13 is recovered in the suction chamber 17.

Next, the operation of the enlargement units 51 and 55 will be described with reference to FIG. FIG. 4 is a graph showing the transition of the volume efficiency with respect to the operating rotational speed by comparing the conventional one 57 having no enlarged portion and the one 59 of the present embodiment.
Since the force by which the refrigerant gas conveys the lubricating oil is proportional to the square of the inflow speed, sufficient lubricating oil is conveyed at high speed rotation (high operation speed Hz). Therefore, since sufficient oil seals are formed also in the enlarged portions 51 and 55, the volume efficiency similar to the conventional one (that is, the refrigerant gas to be discharged) is combined with the fact that most of the other parts are at the same interval as the conventional one. Equivalent to the amount).
When the number of revolutions of operation decreases and S1 is reached, the amount of the lubricating oil 47 carried by the refrigerant gas is reduced, and there is a slight influence on the whole, and the volume efficiency of the conventional one also starts to decrease slightly. In this tendency, a decrease in volumetric efficiency is observed with the conventional one as well as a decrease in the operating rotational speed. In addition to the decrease in volumetric efficiency, the minimum operation speed S0 is set in order to lubricate the bearings and ensure lubricity between the scrolls. Although the above-described compressor has been described as having a structure in which the suction gas directly enters the compression chamber, naturally, the same reduction is also achieved in the compressor having a structure in which the suction gas once enters the housing and then enters the compression chamber.

In the present embodiment, the oil seal becomes insufficient at the winding end at the widest interval at the operating rotational speed S1. As a result, the refrigerant gas sucked into the compression chamber P leaks, so that the volumetric efficiency is slightly lower than the conventional one.
When the operating rotational speed further decreases, the region where the oil seal becomes insufficient gradually expands from the end of winding toward the center, so that the refrigerant gas leakage gradually increases.
At the minimum operation speed S0, leakage occurs in the entire area of the enlarged portions 51 and 55, and the volumetric efficiency is less than half of the conventional one.
Note that the volumetric efficiency at the minimum operating rotational speed S0 is substantially determined by the area M of the enlarged portions of the enlarged portions 51 and 55 as shown in FIG. 3, so that the volumetric efficiency can be arbitrarily adjusted by adjusting the area M. be able to.

Hereinafter, the operation and effect of the scroll compressor 1 according to the present embodiment will be described.
According to the scroll compressor according to the present embodiment, since the fixed scroll spiral body 19b and the orbiting scroll spiral body 21b are provided with the enlarged portions 51 and 55 having a larger interval than the center side on the winding end side. When the operating speed of the scroll compressor 1 decreases and the amount of lubricating oil carried into the compression chamber P becomes a predetermined amount or less, even if the oil seal is sufficiently maintained except for the enlarged portions 51 and 55, The oil seals at the enlarged portions 51 and 55 are not sufficiently formed.
If the oil seals of the enlarged portions 51 and 55 are not sufficiently formed, the refrigerant gas leaks from the enlarged portions 51 and 55, so that the amount of refrigerant gas sucked into the compression chamber is reduced. For this reason, the amount of refrigerant gas discharged from the compression chamber P can be reduced.

Since the leakage of the refrigerant gas in the enlarged portions 51 and 55 increases as the operating speed decreases, the range of the operating speed in which the oil seal is formed in a portion other than the enlarged portions 51 and 55 (above the minimum rotational speed). ), It is possible to further reduce the amount of refrigerant gas discharged at a low operation speed as compared with the conventional case.
As described above, the amount of refrigerant gas discharged at a low operation speed can be reduced, so that only the scroll compressor 1 can cope with a small amount of refrigerant required, for example, during air conditioning in an intermediate period. There is sex.
In this case, for example, it is not necessary to install equipment for bypassing excess refrigerant gas, so that the manufacturing cost of the air conditioner can be reduced.

Moreover, since the expansion parts 51 and 55 are formed in the substantially 1/2 turn part of the winding end side of the turning scroll spiral body 21b and the fixed scroll spiral body 19b, the refrigerant gas which leaks is hardly compressed. Become. For this reason, the loss of power required for compression is not increased.
In addition, if the expansion parts 51 and 55 are formed in the part below one turn of the winding end side of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b, the compression chamber P formed on the outermost side is the orbiting scroll spiral body. Since the refrigerant gas does not leak after the suction is closed by the winding end of 21b or the fixed scroll spiral body 19b, it is possible to prevent the power that compressed the refrigerant gas from being wasted.

Furthermore, since the enlarged portions 51 and 55 are formed so that the intervals gradually increase toward the winding end sides of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b, the winding end ends as the operation rotational speed decreases. The oil seal gradually becomes insufficient from the side toward the inside.
For this reason, since the portion where the refrigerant gas leaks gradually from the operating speed S1 that accompanies the decrease in the operating speed, the amount of discharged refrigerant gas can be gradually reduced.
Since the discharge refrigerant gas amount can be gradually reduced, the discharge refrigerant gas amount can be easily adjusted.
Moreover, since the leakage of the refrigerant gas proceeds from the winding end end side where the progress of compression is small, power loss can be reduced.
Furthermore, since the enlarged portions 51 and 55 are formed by lowering the height of the winding end side of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b, the processing range is narrow and can be easily processed. In addition, since only the height is changed, the part inspection process is facilitated.

In the present embodiment, the enlarged portions 51 and 55 are provided at the respective winding end ends of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b. May be.
If it carries out like this, since the reduction effect of a refrigerant | coolant gas amount will be substantially half compared with what was provided in both, it is good to use for the thing which does not require so big reduction.

Further, in the present embodiment, the turning-side lower portion 49 and the fixed-side lower portion 53 are formed so as to gradually decrease linearly from the central tooth height H1 to the winding end tooth height H2. Further, it may be changed in a curved line, or as shown in FIG. Furthermore, you may form by arbitrary shapes.
FIG. 4 shows a change in volumetric efficiency of the portion 61 in which the enlarged portion 65 is constituted by the step lower portion 63.
The enlarged area of the enlarged portion 65 is substantially the same as the area M of the enlarged portions 51 and 55. For this reason, the space | interval of the expansion part 65 is substantially the same as the space | interval of the intermediate part of the length along the spiral curve of the expansion parts 51 and 55. FIG.

For this reason, the leakage of the refrigerant gas from the enlargement unit 65 does not occur until the operating rotational speed S2 is lower than that of the enlargement units 51 and 55. However, once it occurs, the refrigerant gas leaks all at once in the entire enlarged portion 65, so that the volumetric efficiency of the refrigerant gas rapidly changes (reduces) up to the minimum operation speed S0.
Therefore, it is difficult to adjust the operating rotational speed to obtain the required amount of refrigerant gas discharged, compared with the case where the enlarged portion gradually increases toward the winding end, but the volumetric efficiency should be kept high up to the low operating rotational speed. Can do.

In the present embodiment, the enlarged portions 51, 55, and 65 are formed by reducing the tooth heights of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b. However, the present invention is not limited to this, and the fixed scroll is not limited thereto. The portions corresponding to the winding end ends of the end plate 19a and the orbiting scroll end plate 21a may be scraped to form an enlarged portion.
Further, an enlarged portion is formed by combining the reduction of the tooth height of the orbiting scroll spiral body 21b and the fixed scroll spiral body 19b and the removal of the portions corresponding to the winding end ends of the fixed scroll end plate 19a and the orbiting scroll end plate 21a. You may make it do.

It is sectional drawing which shows the whole schematic structure of the scroll compressor concerning one Embodiment of this invention. 1 is a perspective view showing an overall schematic configuration of a turning scroll according to an embodiment of the present invention. It is an expanded view which shows the state which expand | deployed the turning scroll spiral body concerning one Embodiment of this invention. It is a graph which compares and shows transition of the volume efficiency with respect to the driving | running rotation speed of one Embodiment of this invention, and the conventional one. It is a perspective view which shows the whole schematic structure of another embodiment of the turning scroll of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Scroll compressor 19 Fixed scroll 19a Fixed scroll end plate 19b Fixed scroll spiral body 21 Orbiting scroll 21a Orbiting scroll end plate 21b Orbiting scroll spiral body 51, 55, 65 Expansion part

Claims (4)

A fixed scroll having a spiral fixed side wall provided upright on one side surface of the fixed side end plate;
A swirl having a swirl-shaped swirl side wall standing on one side of a swirl side end plate, and supported so as to be capable of a revolving swirl so as to form a compression chamber by engaging the swirl side wall and the fixed side wall. A scroll compressor having a scroll,
At least one of the fixed side wall body and the swivel side end plate and the swivel side wall body and the fixed side end plate have at least one end of winding of the fixed side wall body or the swivel side wall body. A scroll compressor characterized in that, on the side, an enlarged portion having a larger interval than the center side is provided.   2. The scroll compressor according to claim 1, wherein the enlarged portion is formed in a portion of the fixed side wall or the turning side wall that is less than one turn on the winding end side.   3. The scroll compressor according to claim 1, wherein the enlarged portion is formed so that an interval gradually increases toward a winding end side of the fixed side wall body or the turning side wall body. The scroll compressor according to any one of claims 1 to 3, wherein the enlarged portion is formed by lowering the height of the fixed side wall body or the turning side wall body.

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