JP2020186710A - Scroll compressor - Google Patents

Abstract

To realize the shape of the end plate surface of a fixed scroll by which pushing force of an orbiting scroll to the fixed scroll is reduced, while suppressing overturning of the orbiting scroll, in a scroll compressor having an asymmetric wrap structure in which a working chamber on the orbiting outer line side and a working chamber on the orbiting inner line side are different in volume at the completion of suction and having discharge start timing also different in each working chamber.SOLUTION: Setting, as a base point, a fixed scroll inner line position corresponding to the wrapping end of an orbiting warp of a working chamber on the orbiting outer line side at the completion of suction, and setting, as a base line, a half straight line extending from the center of a fixed scroll toward the base point, an extension portion, in which an end plate surface on the fixed scroll side extends to the outer diameter side, is provided within a range of 45° or more in the orbiting direction of the orbiting scroll from the base line and 45° or more in the reverse orbiting direction.SELECTED DRAWING: Figure 3

Description

The present invention relates to a scroll compressor that handles carbon dioxide, a refrigerant, air, and other compressible gases, and particularly reduces the sliding loss generated in the end plate sliding portion of a swivel scroll and a fixed scroll to achieve high energy. For scroll compressors with efficiency and high reliability.

Patent Document 1 aims at "providing a scroll-type fluid machine capable of reducing the overturning moment with respect to a movable scroll without increasing the manufacturing cost" (paragraph 0014), and "fixing at the start of discharge". Let X be a half straight line passing from the center of the scroll to the center of the movable scroll, let Y be a half straight line rotated 90 ° in the rotation direction with respect to the half straight line X starting from the center of the movable scroll, and be surrounded by the half straight line X and the half straight line Y. When the specified area is the first area and the area rotated by 90 ° in the rotation direction is the second area, the third area, and the fourth area in order, the thrust antiverse that becomes the farthest from the center of the movable scroll at the start of ejection. A reaction force receiving portion for receiving the force acting point is provided in the second region of the movable scroll end plate "(paragraph 0016), and" the region where the thrust reaction force acting point is farthest from the center of the movable scroll is the second region. ... Since the reaction force receiving portion provided in the second region reliably receives the point of action of the thrust reaction force, it is possible to effectively prevent the tilt of the movable scroll at the start of ejection. "(Paragraph 0017). ), Etc. are disclosed.

Japanese Unexamined Patent Publication No. 10-184567

In a scroll compressor, a fixed scroll and a swivel scroll are pressed to form an operating chamber. The pressing side may be either a fixed scroll or a swivel scroll, or both may be pressed against each other, but here, the case where the working chamber is constructed by pressing the swivel scroll against the fixed scroll will be described. To do. On the non-fixed scroll side of the swivel scroll, in order to press the swivel scroll against the fixed scroll, there is a high-pressure part that has an almost discharge pressure atmosphere in the center of the swivel scroll, and an intermediate pressure between suction pressure and discharge pressure on the outer peripheral part. In many cases, a back pressure chamber is provided, which has an atmosphere (hereinafter referred to as back pressure). In some cases, suction pressure is used instead of back pressure. Since the airtightness of the working chamber is important in the compression operation, it is necessary to properly press the swivel scroll against the fixed scroll. However, if the pressing is excessive, the sliding loss due to the turning motion of the turning scroll in the compression operation becomes excessive, and if the pressing is insufficient, the airtightness of the operating chamber cannot be ensured, and energy loss occurs in any case. In the worst case, if the pressing is excessive, the sliding surfaces of the fixed scroll and the swivel scroll (hereinafter referred to as the end plate surface) are seized and the operation becomes inoperable.

The pushing force required for the turning scroll is determined by the balance between the turning scroll pushing force due to the discharge pressure, back pressure, or suction pressure from the non-fixed scroll side and the turning scroll pushing force due to the operating chamber pressure on the fixed scroll side. Generally, the points of action of the pushing force and the pushing force are not on the same straight line, and a moment is generated. In addition, a moment is generated due to the gas load in the operating chamber in the direction orthogonal to the pushing and pushing direction. Since these moments are moments that have the effect of pulling the turning scroll away from the fixed scroll (hereinafter referred to as the overturning moment), not only the pushing force is made larger than the pushing force, but also the pushing force is set to a size that can overcome the overturning moment. There is a need.

Here, Patent Document 1 describes an operating chamber formed by a swirling lap outer line and a fixed lap extension (hereinafter referred to as a swirling outer line side operating chamber) and an operating chamber formed by a swirling lap extension and a fixed lap outer line (hereinafter referred to as a swirling lap extension). , Called the turning extension side operating chamber), is a so-called symmetric lap structure scroll compressor that has the same volume when suction is completed. Moreover, the scroll compressor of Patent Document 1 is premised on the case where the discharge start timing is the same for the turning outer line side operating chamber and the turning extension side operating chamber. However, in recent scroll compressors, the so-called asymmetric wrap structure, in which the volumes of the swivel external line side operating chamber and the swivel extension side operating chamber are different when suction is completed, is the mainstream. In many cases, the discharge start timing is not the same. Since the magnitude of the pushing force and the point of action change greatly depending on the pressure state in the operating chamber, the required pushing force cannot be reduced by the asymmetric wrap structure in the configuration disclosed in Patent Document 1.

An object of the present invention is an asymmetric lap structure in which the volume at the completion of suction of the turning outside line side operating chamber and the turning extension side operating chamber is different, and the discharge start timing is also different in each operating chamber. The purpose is to reduce the pushing force of the turning scroll to the fixed scroll while suppressing overturning.

In order to solve the above problems, the features of the present invention are a fixed scroll having a fixed end plate and a fixed lap erected on the fixed end plate, a swivel scroll having a swivel end plate and a swirl lap standing on the swivel end plate, and a swivel scroll that swings. The working chamber includes a fixed scroll and an operating chamber formed by meshing the swivel scroll, and the working chamber includes a swivel outer line side working chamber formed by the outer line of the swivel lap and the extension of the fixed lap, and the swivel lap. It has a turning extension side operating chamber formed by an extension and an outside line of the fixed lap, and the turning outside line side working chamber and the turning extension side working chamber have different volumes when suction is completed and also have different discharge start timings. In the scroll compressor, the end plate surface on the fixed scroll side that slides with the swivel scroll has an expansion portion that expands to the outer diameter side at a predetermined location in the circumferential direction, and the predetermined location is when suction is completed. The extension position of the fixed scroll corresponding to the winding end of the turning lap of the turning outside line side operating chamber in the above is used as the base point, and the half straight line extending from the center of the fixed scroll toward the base point is used as the base line. The range is 45 ° or more in the turning direction of the turning scroll and 45 ° or more in the reverse turning direction.

According to the present invention, even in a scroll compressor having an asymmetric lap structure and having different discharge start timings between the turning outside line side operating chamber and the turning extension side operating chamber, it is necessary to press the turning scroll against the fixed scroll. The pushing force (required pushing force) can be reduced. This makes it possible to realize a scroll compressor with high energy efficiency and high reliability.

The whole view of the scroll compressor which concerns on Example 1 of this invention. FIG. 3 is a meshing diagram of a fixed scroll and a swivel scroll according to a first embodiment of the present invention. The block diagram of the fixed scroll which concerns on Example 1 of this invention. The block diagram of the turning scroll which concerns on Example 1 of this invention. It is explanatory drawing of the required pushing force reduction effect of the end plate surface expansion part of the fixed end plate which concerns on Example 1 of this invention. The explanatory view of the necessary pushing force reduction effect of the suction expansion groove which concerns on Example 1 of this invention. The block diagram of the fixed scroll which concerns on Example 2 of this invention.

Hereinafter, specific examples of the scroll compressor of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals indicate the same or corresponding parts.

<Example 1>
The first embodiment will be described with reference to FIGS. 1 to 6. First, the overall configuration of the scroll compressor according to the first embodiment will be described with reference to FIG. In this embodiment, a high-pressure chamber type scroll compressor in which the compression mechanism unit 2 and the drive unit 3 are housed in the casing 4 and the discharge pressure is set in the casing 4 is shown as an example.

The basic configuration of the compression mechanism unit 2 includes a fixed scroll 5, a swivel scroll 6, and a frame 7, and the frame 7 is fixed to the casing 4. The fixed scroll 5 has a fixed end plate 5b, a fixed wrap 5a standing on the fixed end plate 5, a fixed wrap tooth bottom 5c, a fixed wrap tooth tip 5d, and a discharge port 5e. On the other hand, the swivel scroll 6 has a swivel end plate 6b, a swivel lap 6a standing on the swivel end plate 6, a swivel lap tooth bottom 6c, a swivel lap tooth tip 6d, and a discharge pressure portion 6e. The discharge pressure portion 6e of the swivel scroll is arranged on the non-fixed scroll side, and constitutes a part of the refueling path which is the discharge pressure as described later.

The basic configuration of the drive unit 3 that swivels and drives the swivel scroll 6 is the main components of the stator 8a and rotor 8b, the crankshaft 9, and the rotation prevention mechanism of the swivel scroll 6 when the radial motor 8 is used as an example of the rotary drive means. The old dam ring 10, which is a component, the shaft support portion 11 that rotatably engages the frame 7 and the crankshaft 9, and the eccentric pin portion 9a of the swivel scroll 6 and the crankshaft 9 are aligned in the thrust direction, which is the rotation axis direction. It is composed of a shaft support portion 12 of a swivel scroll that is movably and rotatably engaged, and a shaft support portion 13 provided at the lower part of the crankshaft 9. The old dam ring 10 is arranged together with the swivel scroll 6 in the space 14 composed of the frame 7 and the fixed scroll 5. Of the two orthogonal sets of key portions formed on the old dam ring 10, one set has a key groove (not shown) formed in the frame 7, and the remaining one set has an old dam key 6f formed on the back side of the swivel lap 6a. Glide. The space 14 is a space adjusted to a pressure between the suction pressure and the discharge pressure (hereinafter referred to as a back pressure chamber). The pressure in the space 14 may be a suction pressure. Further, as a refueling system, the lubricating oil 15 stored in the lower part of the casing 4 is passed through the refueling pipe 16 fixed to the crankshaft 9 and the refueling hole 9b provided in the crankshaft 9, and the compression mechanism 2 and each shaft are supported. It is supplied to units 11, 12, and 13. At the time of refueling, a refueling path is formed which passes through the discharge pressure portion 6e on the back surface of the swivel scroll with almost the discharge pressure.

Next, the compression operation will be described. The crankshaft 9 fixed to the rotor 8b rotates as the rotor 8b rotates. The swivel scroll 6 is movably engaged with the eccentric pin portion 9a of the crankshaft so as to be movable in the thrust direction, and the rotational movement of the crankshaft 9 is caused by the rotation prevention mechanism, the old dam ring 10. Converted into exercise. In the operating chamber 17 formed by meshing the fixed scroll 5 and the swivel scroll 6, the swivel scroll 6 swivels to reduce the volume and perform a compression operation. In the compression operation, the working fluid is sucked into the working chamber 17 via the suction port 18 and the suction space 19 as the swirling scroll 6 swivels. The sucked working fluid communicates with the discharge port 5e through the compression stroke, and is discharged via the discharge space 20 and the discharge port 21. In order to perform the compression operation with a small energy loss, the following conditions are required when the fixed scroll 5 and the swivel scroll 6 are meshed and swiveled. The conditions include ensuring necessary and sufficient airtightness between the suction space 19 and the operating chamber, between the operating chambers having different pressure states, and between the operating chamber and the discharge port 5e as much as possible, and the fixed scroll 5 Proper pressing of the swivel scroll 6 to.

Further, the meshing state of the fixed scroll 5 and the swivel scroll 6 will be described in detail with reference to FIGS. 2 to 4. Here, the end plate surface is a part of the end plate that is in sliding contact when the fixed scroll 5 and the swivel scroll 6 mesh with each other to form the operating chamber 17, and the end plate surface 5f of the fixed scroll 5 and the end plate surface 6g of the swivel scroll 6 are formed. It exists in each as. FIG. 2 shows a state in which the swivel outer line side operating chamber 22 composed of the outer line of the swivel lap 6a and the extension of the fixed lap 5a is in mesh with the swivel scroll 6 and the fixed scroll 5 at the position where the suction is completed. The case where the crank angle is 180 ° is shown. FIG. 3 shows the main configuration of the fixed scroll 5, and FIG. 4 shows the main configuration of the swivel scroll 6. These are scroll compressions of an asymmetric wrap structure in which the above-mentioned swivel external line side operating chamber 22 and the swivel internal line side operating chamber 29 composed of the internal line of the swivel wrap 6a and the external line of the fixed wrap 5a have different volumes when suction is completed. Shows the machine. In this embodiment, the turning extension side operating chamber 29 completes suction 180 ° after the suction completion of the turning outside line side operating chamber 22 (0 ° in crank angle). The direction of rotation of the crankshaft during compression is the direction of 360 ° → 0 °, and the positive and negative notations are reversed from the turning direction.

By the way, the end plate surface 5f on the fixed scroll side of this embodiment has an expansion portion 5g (cross hatch portion) that expands to the outer diameter side at a “predetermined location” in the circumferential direction. Here, the fixed scroll extension position corresponding to the end of winding of the swivel lap 6a of the swivel outer line side operating chamber 22 at the completion of suction is set as the base point 23, and the half straight line extending from the center of the fixed scroll 5 toward the base point 23 is set as the base line 24. To do. In that case, the above-mentioned "predetermined location" is in the range of 45 ° or more (crank angle 135 ° or less) in the turning direction of the turning scroll 6 and 45 ° or more (225 ° or more in the crank angle) in the reverse turning direction from the baseline 24. is there. Further, the expansion portion 5g of the end plate surface 5f of the fixed end plate is divided into four in the turning direction and shown in FIG. With respect to the baseline 24, the expansion part 5g1 up to 45 ° in the turning direction, then the expansion part 5g2 up to 90 °, and conversely, the expansion part 5g3 up to 45 ° in the counter-turning direction, and then the expansion part up to 90 °. Part 5g4.

The inner circumference 5h of the expansion portion 5g in this embodiment is located on the innermost circumference locus of the outer circumference 6h of the swivel end plate when the swivel scroll 6 performs a swivel motion. Further, the outer peripheral 5i of the expansion portion 5g in this embodiment is located on the outermost peripheral locus of the outer peripheral 6h of the swivel end plate when the swivel scroll 6 performs a swivel motion. If the expansion portion 5g is formed so as to extend from the base point 23 to the outer diameter side in the radial direction beyond the thickness of the swirl wrap 6a, the minimum airtightness can be maintained. Further, the sliding loss can be minimized by forming the expansion portion 5g inside the sum of the radius of the swivel end plate 6b and the swivel radius of the swivel scroll 6 (the amount of eccentricity of the crankshaft). Here, the fixed end plate surface 25 of the prior art is shown by a broken line.

Further, a back pressure adjusting portion 27 for adjusting the back pressure, which is the pressure of the back pressure space 14, and a suction expansion groove 28 communicating with the suction pressure are provided. The suction expansion groove 28 is formed on the end plate surface on the fixed scroll side and communicates with the suction space in the operating chamber, and is configured with an angle width of 28a. By providing the suction expansion groove 28, the withdrawal tolerance of the swivel scroll can be improved as described later.

Further, in this embodiment, the range of 90 ° or more and 180 ° or less in the turning direction of the swivel scroll and 90 ° or more and 180 ° or less in the reverse turning direction from the baseline 24 is set to 6 g of the end plate surface of the swivel end plate and the end plate surface of the fixed end plate. It is configured as a region 26 that does not slide with 5f. That is, the radial length 5j of the end plate surface 5f of the fixed end plate in the above range is larger than the tooth width of the fixed lap 5a and the swivel lap 6a, and the outer circumference of the swivel end plate is found to be the innermost locus when the swivel motion is performed. It is configured to be small (the area area is smaller than that of the fixed end plate surface 25 of the prior art). By providing this non-sliding region, the required pushing force can be further reduced.

Next, the action of reducing the required pushing force when pressing the swivel scroll 6 against the fixed scroll 5, which is obtained by devising the shape of the end plate surface 5f on the fixed scroll side as in the present embodiment, will be described.

First, the pushing force that presses the swivel scroll 6 against the fixed scroll 5 that acts from the back surface of the swivel end plate 6b will be described. When the pushing force of the swivel scroll 6 is insufficient, the swivel scroll 6 is separated from the fixed scroll 5, and the swivel scroll 6 cannot form the fixed scroll 5 and the operating chamber 17 which is a closed space. The disengagement of the swivel scroll 6 may occur at the full rotation angle of the crankshaft, but may also occur at a partial angle due to insufficient pushing force. In any case, the lack of airtightness leads to an increase in energy loss and a decrease in reliability. On the contrary, when the pushing force of the swivel scroll is excessive, the pressing force of the fixed scroll 5 and the swivel scroll 6 becomes excessive, and the worst seizure occurs, and the reliability is also impaired.

Here, the pushing force additional action due to the provision of the expansion portion 5g on the end plate surface 5f of the fixed end plate will be described with reference to the calculation example shown in FIG. In the calculation example, the degree of withdrawal of the swivel scroll was examined according to the permissibility of the swivel scroll withdrawal in three cases having different end plate surface shapes. The structural specifications and pressure specifications related to the pushing force, pushing force, and capsizing moment in the swivel end plate are basically the same in all three cases. However, in the suction expansion groove 28, the angle width 28a is about 1/3 the size of the example shown in FIG. 3 and is the same in 3 cases, and the width is the same in the other 2 cases with respect to the fixed end plate surface 25 of the prior art. Is about 1.8 times. Further, at the crank angle, the suction completion of the swivel extension side operating chamber 22 is 180 °, the discharge start of the swivel extension side operating chamber 22 is 64 °, the discharge start of the swivel extension side operating chamber 29 is 13 °, and the swivel extension side operating chamber 29. The suction completion of is 0 °. In the calculation, the balance between the pushing force, the pushing force, and the overturning moment in the swivel end plate is calculated for each crank angle, and it is determined whether or not the point of action of the push-up direction resultant force exceeds the withdrawal limit of the swivel scroll. The swivel scroll release limit means a limit position when the reaction force on the fixed end plate surface generated by pressing the swivel scroll 6 against the fixed scroll 5 always occurs in the direction of pushing down the swivel end plate. In addition, the turning scroll withdrawal tolerance indicates the degree of separation between the point of action of the push-up direction resultant force and the turning scroll withdrawal limit at the shortest distance. If it is a positive value, the turning scroll withdrawal limit is not reached, and the reaction force on the fixed end plate surface is always generated in the direction of pushing down the turning end plate, so that the turning scroll does not come off. If there is a crank angle that is a negative value, there is a crank angle that causes the turning scroll to come off.

In the case of the shape of the end plate surface 5f on the fixed scroll side in this embodiment, the action of adding the pushing force near the crankshaft rotation angle (crank angle of 90 to 0 °) where the pushing force of the swivel scroll 6 is most insufficient. It turned out that there was.

FIG. 5 shows the results of the three types of fixed end plate surfaces, with the swivel scroll release tolerance on the vertical axis and the crankshaft rotation on the horizontal axis. The three types of fixed end plate surfaces are a conventional fixed end plate surface 25 and a end plate having an extension portion of 5 g (hereinafter referred to as a 45 ° end plate surface shape) up to ± 45 ° (5 g 1, 5 g 3) as a + display of the turning direction. A surface and a end plate surface having an extension portion of 5 g (hereinafter referred to as a 90 ° end plate surface shape) up to ± 90 ° (5 g 1 to 5 g 4). The smaller the turning allowance tolerance on the vertical axis, the closer the point of action of the push-up direction resultant force is to the turning scroll leaving limit.

From FIG. 5, the swivel scroll withdrawal tolerance is larger near the crankshaft rotation angle where the pushing force of the swivel scroll 6 is insufficient for both the 45 ° end plate surface shape and the 90 ° end plate surface shape than the conventional end plate surface shape. I found out. Furthermore, it was also found that the 90 ° end plate surface shape has a larger swivel scroll detachment tolerance than the 45 ° end plate surface shape. From the above, the expansion portion 5g of the end plate surface 5f of the fixed end plate has an effect of suppressing the detachment of the swivel scroll 6. That is, even if the pushing force in the 90 ° end plate surface shape or the 45 ° end plate surface shape is reduced until the minimum value of the swivel scroll detachment tolerance in the prior art end plate surface shape is reached, the swivel scroll detachment does not occur. Become. Therefore, if the 90 ° end plate surface shape or the 45 ° end plate surface shape is used, proper pressing can be performed even if the back pressure is lowered to reduce the pushing force, so that the required pushing force itself can be reduced. The shape of the end plate surface 5f of the fixed end plate in this embodiment can reduce the required pushing force itself, but increases the area of the end plate, which causes an increase in sliding loss between the fixed scroll 5 and the swivel scroll 6. Therefore, when expanding the shape of the end plate surface 5f of the fixed end plate in the turning direction, it is preferable that it is ± 45 ° or more, but the upper limit is a trade-off with the sliding loss caused by the large end plate area. It will be decided.

Next, the effect of the suction expansion groove 28 will be described. As described above, by providing the expansion portion 5g on the end plate surface 5f of the fixed end plate, the suction expansion groove 28 can be easily formed. However, if the 90 ° end plate surface shape has a large expansion region, the suction expansion groove 28 becomes more visible. It can be configured large. The angle width 28a shown in FIG. 3 can be further expanded by about 10%. In the 90 ° end plate surface shape, the withdrawal tolerance of the swivel scroll 6 was examined in the case of the suction expansion groove 28 shown in FIG. 5 and the case where the angle width of the suction expansion groove 28 was further widened by 10% from that of FIG. The results are shown in FIG. The withdrawal tolerance of the turning scroll was further increased in the sections where the crank angles were 115 to 0 ° and 360 to 180 °. It was found that by expanding the suction expansion groove 28 with a 90 ° end plate surface shape, the withdrawal tolerance of the swivel scroll is improved in a wide crank angle range.

In this embodiment, the required pushing force that enables proper pressing is reduced by providing the fixed end plate with an expansion portion of 5 g, but the end plate surface 6 g of the swivel end plate and the end plate surface 5f of the fixed end plate are not slid. By forming a moving region, the required pushing force can be further reduced. Further, if the suction expansion groove 28 is provided, the release tolerance of the swivel scroll can be improved in a wide crank angle range, so that the required pushing force can be further reduced. From the above, since the required push-up force itself can be reduced, the airtightness of the operating chamber can be ensured by the push-up force of the small swivel scroll. As a result, it is possible to realize a scroll compressor that can secure high energy efficiency, prevent over-pressing of the end plate surface, and secure high reliability.

<Example 2>
The configuration of the fixed scroll in the second embodiment will be described with reference to FIG. 7. The description of the parts common to the first embodiment will be omitted. There are two differences from the first embodiment, one is that the outer circumference 30i of the expansion portion 30g of the fixed end plate is the same as the inner circumference of the fixed seat surface 31 of the fixed scroll 30, and the other is that This is the point where the expansion in the turning direction exceeds + 90 °. The first feature is that the outer circumference 30i of the expansion portion 30g is the same as the inner circumference of the fixed seat surface 31, so that the diameter of the fixed scroll 30 can be reduced. The second feature is that the expansion in the turning direction exceeds + 90 °, so that the sliding loss does not become excessive in the case of a scroll compressor that mainly operates at low speed, so the expansion part 30 g of the fixed end plate is widened. It is possible to reduce the required pushing force itself.

1: Scroll compressor, 2: Compression mechanism, 3: Drive, 4: Casing, 5, 30: Fixed scroll, 5a, 30a: Fixed wrap, 5b, 30b: Fixed end plate, 5c, 30c: Fixed wrap tooth bottom , 5d, 30d: Fixed wrap tooth tip, 5e, 30e: Discharge port, 5f, 30f: End plate surface, 5g, 30g: End plate expansion part, 5h, 30h: Inner circumference of expansion part, 5i, 30i: Outer circumference of expansion part , 5j, 30j: Radial length, 5k, 30k: Center, 6: Swivel scroll, 6a: Swivel lap, 6b: Swivel end plate, 6c: Swivel lap tooth bottom, 6d: Swivel lap tooth tip, 6e: Discharge pressure part , 6f: Oldam key, 6g: End plate surface, 6h: End plate outer circumference, 6i: Center, 7: Frame, 8: Radial motor, 8a: Stator, 8b: Rotor, 9: Crank shaft, 9a: Eccentric pin part, 9b: Refueling hole, 10: Oldam ring, 11, 12, 13: Shaft support, 14: Back pressure space, 15: Lubricating oil, 16: Refueling pipe, 17: Operating chamber, 18: Suction port, 19: Suction space, 20 : Discharge space, 21: Discharge port, 22: Swirling outside line side operating chamber, 23: Base point, 24: Base line, 25: Fixed end plate surface of the prior art, 26: Non-sliding area, 27: Back pressure adjusting part, 28: Suction expansion groove, 28a: Angle width of suction expansion groove, 29: Swivel extension side operating chamber

Claims (8)

A fixed scroll having a fixed end plate and a fixed wrap standing on the fixed end plate, a swivel scroll having a swivel end plate and a swirl wrap standing on the swivel end plate, and a swivel scroll having a swivel movement, and an operation formed by engaging the fixed scroll and the swivel scroll. With a room,
The operating chamber includes a swivel outer line side working chamber formed by the outer line of the swivel lap and the extension of the fixed lap, and a swivel extension side working chamber formed by the inner line of the swivel lap and the outer line of the fixed lap. Have and
In a scroll compressor, the swivel extension side operating chamber and the swivel extension side operating chamber have different volumes and different discharge start timings when suction is completed.
The end plate surface on the fixed scroll side that slides with the swivel scroll has an extension portion that expands to the outer diameter side at a predetermined position in the circumferential direction.
The predetermined location is based on the extension position of the fixed scroll corresponding to the end of winding of the swivel lap in the swivel external line side operating chamber when suction is completed, and extends from the center of the fixed scroll toward the base point. A scroll compressor having a half straight line as a baseline and having a range of 45 ° or more in the turning direction of the turning scroll and 45 ° or more in the reverse turning direction from the baseline. The scroll compressor according to claim 1, wherein the swivel end plate and the swivel end plate are within a range of 90 ° or more and 180 ° or less in the swivel direction of the swivel scroll and 90 ° or more and 180 ° or less in the reverse swivel direction from the baseline. A scroll compressor characterized by forming a non-sliding region of a fixed end plate. The scroll compressor according to claim 1 or 2, wherein a groove communicating with a suction space in the operating chamber is provided on the end plate surface on the fixed scroll side. The scroll compressor according to any one of claims 1 to 3, wherein the expansion portion of the end plate surface on the fixed scroll side is on the outer diameter side of the innermost circumferential locus when the outer circumference of the swivel end plate performs a swivel motion. A scroll compressor characterized by being formed extending to. The scroll compressor according to any one of claims 1 to 3, wherein the expansion portion of the end plate surface on the fixed scroll side is formed on the inner diameter side of the outermost outer peripheral locus when the outer circumference of the swivel end plate performs a swivel motion. A scroll compressor characterized by being. The scroll compressor according to any one of claims 1 to 3, wherein the expansion portion of the end plate surface on the fixed scroll side is formed so as to extend in the radial direction beyond the thickness of the swivel wrap. Scroll compressor. The scroll compressor according to any one of claims 1 to 3, wherein the expansion portion of the end plate surface on the fixed scroll side is formed on the inner diameter side of the sum of the radius of the swivel end plate and the swivel radius of the swivel scroll. A scroll compressor characterized by being. The scroll compressor according to claim 2, wherein the non-sliding region is formed on the inner diameter side of the innermost circumferential locus when the outer circumference of the swivel end plate performs a swivel motion. ..

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