JP2017186948A - Scroll compressor and air conditioning device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor applying a scroll structure configured under consideration of a gas pressure inside of a compressor chamber and thermal expansion of a scroll in operation, to prevent enlargement of a clearance gap between a fixed-side lap portion and a movable-side lap portion, and to reduce refrigerant leakage loss.SOLUTION: A scroll compressor has a fixed scroll 30 in which a spiral-shaped fixed-side lap portion is vertically disposed, and a movable scroll 40 in which a spiral-shaped movable-side lap portion engaged with the fixed-side lap portion is vertically disposed. Here, winding end portions 32a, 42a of the spiral shapes of the lap portions have inverse-taper shapes, and further winding intermediate portions as parts respectively between the winding start portions 32b, 42b and the winding-end portions of the lap portions have the inverse-taper shapes having a taper rate smaller than that of the winding-end portions.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a scroll compressor and an air conditioner including the same.

  Conventionally, there is a scroll compressor having a fixed scroll and a movable scroll. In the fixed scroll, a spiral fixed side wrap portion is erected on one surface of the fixed side plate portion. The movable scroll is disposed so as to be able to turn facing the fixed scroll, and a spiral movable side wrap portion that is engaged with the fixed side wrap portion is provided on one surface of the movable side plate portion.

  In such a scroll compressor, as shown in Patent Document 1 (Japanese Patent Publication No. 63-15443), in order to improve the strength of the root portion of the fixed side and the movable side wrap portion, the fixed side and the movable side wrap are provided. A structure in which the tooth thickness at the root portion of the part is increased is employed.

  However, in a scroll compressor such as Patent Document 1, during operation, the gas pressure in the compression chamber formed by the fixed side wrap part and the movable side wrap part is between the fixed side wrap part and the movable side wrap part. Since it acts as a force in a direction away from each other, the gap between the fixed side wrap portion and the movable side wrap portion is enlarged, and there is a possibility that the leakage loss of the refrigerant increases.

  Also, in the compression chamber, since the gas temperature increases from the winding end of the wrap portion toward the winding start end, the movable scroll is deformed into a convex shape toward the root portion of the fixed scroll due to thermal expansion, It affects the gap between the fixed side wrap portion and the movable side wrap portion. In particular, when a refrigerant such as R32 that tends to increase the discharge gas temperature is used, the movable scroll is greatly deformed in a convex shape toward the root portion of the fixed scroll due to thermal expansion under an operation condition of a high compression ratio. This has a great influence on the gap between the fixed side wrap portion and the movable side wrap portion.

  When the influence of the gas pressure inside the compression chamber during such operation overlaps with the influence of the thermal expansion of the movable scroll, the gap between the fixed side wrap part and the movable side wrap part becomes a spiral shape of the wrap part. Therefore, a refrigerant leakage loss corresponding to this change occurs.

  An object of the present invention is to adopt a scroll structure that takes into account the gas pressure inside the compression chamber during operation and the thermal expansion of the scroll in the scroll compressor, so that there is a gap between the fixed side wrap part and the movable side wrap part. It is to reduce the leakage loss of the refrigerant by suppressing the increase.

  A scroll compressor according to a first aspect includes a fixed scroll and a movable scroll. In the fixed scroll, a spiral fixed side wrap portion is erected on one surface of the fixed side plate portion. The movable scroll is disposed so as to be able to turn facing the fixed scroll, and a spiral movable side wrap portion that is engaged with the fixed side wrap portion is provided on one surface of the movable side plate portion. And the winding end part which is a part including the winding end of a spiral shape among the movable side wrap part and the fixed side wrap part has a reverse taper shape in which the tooth thickness of the tooth tip part is larger than the tooth thickness of the root part. ing. Moreover, the winding intermediate portion, which is the portion between the winding start portion and the winding end portion, which is the portion including the spiral winding start end of the movable side wrap portion and the fixed side wrap portion, is more tapered than the winding end portion. Is a small reverse taper shape. Here, the “taper ratio” is a value obtained by dividing a value obtained by subtracting the tooth thickness of the root portion from the tooth thickness of the tooth tip portion of the wrap portion by the tooth thickness of the tooth tip portion.

  When the influence of the gas pressure inside the compression chamber during operation overlaps with the influence of thermal expansion of the movable scroll, the gap between the fixed side wrap part and the movable side wrap part is from the spiral winding start end of the wrap part. It changes in a complex manner toward the winding end, and tends to be larger on the side of the winding end of the spiral shape of the wrap portion than on the side of the winding start end of the spiral shape of the wrap portion.

  Therefore, here, in anticipation of the combined change tendency of the gap between the lap portions due to the gas pressure in the compression chamber during operation and the thermal expansion of the scroll, the winding end portion of the wrap portion is reversely tapered as described above. In addition, the winding intermediate portion of the wrap portion has a reverse taper shape with a taper ratio smaller than that of the winding end portion.

  As a result, it becomes possible to cancel the complex change tendency of the gap due to the gas pressure inside the compression chamber and the thermal expansion of the scroll during operation, and to suppress the gap between the lap parts from becoming large. The leakage loss of the refrigerant can be reduced.

  In the scroll compressor according to the second aspect, in the scroll compressor according to the first aspect, the reverse tapered shape at the winding end portion has the maximum taper ratio.

  Here, the change tendency is appropriately canceled at the end of winding where there is a possibility that the gap between the lap parts may become the maximum due to the combined change tendency of the gap due to the gas pressure inside the compression chamber during operation and the thermal expansion of the scroll. Thus, an increase in the gap between the wrap portions at the winding end portion can be suppressed, and the leakage loss of the refrigerant can be effectively reduced.

  A scroll compressor according to a third aspect is a scroll compressor according to the first or second aspect, wherein the winding start portion has a straight shape in which the tooth thickness of the root portion and the tooth thickness of the tooth tip portion are the same. It has become. Here, “straight shape” means that the taper ratio is zero (0).

  Here, the change tendency is appropriately canceled at the winding start portion where the gap between the lap portions may be minimized by the combined change tendency of the gap due to the gas pressure in the compression chamber during operation and the thermal expansion of the scroll. Thus, an increase in the gap between the wrap portions at the winding start portion can be suppressed, and the leakage loss of the refrigerant can be effectively reduced.

  A scroll compressor according to a fourth aspect is the scroll compressor according to any one of the first to third aspects, wherein the reverse taper shape in the winding intermediate part is continuously from the winding start part side to the winding end part side. The taper ratio is changing.

  Here, in the winding intermediate part where the gap between the lap parts may change continuously due to the combined change tendency of the gap due to the gas pressure inside the compression chamber during operation and the thermal expansion of the scroll, the change tendency is appropriate. It is possible to effectively reduce the refrigerant leakage loss by suppressing the increase in the gap between the lap portions in the winding intermediate portion.

  The scroll compressor concerning the 5th viewpoint is used in order to compress the refrigerant containing R32 in the scroll compressor concerning either of the 1st-the 4th viewpoint.

  When the refrigerant that tends to increase the temperature of the discharge gas refrigerant as described above is used, the movable scroll is greatly deformed in a convex shape toward the root portion of the fixed scroll due to thermal expansion. It will have a great effect on the gap between the two.

  On the other hand, since the scroll compressor concerning any of the 1st-4th viewpoint is employ | adopted as a scroll compressor here, the gas pressure in the compression chamber inside at the time of operation, and the thermal expansion of a movable scroll This makes it possible to cancel the complex change tendency of the gap between the wrap portions, and to prevent the gap between the wrap portions from increasing.

  An air conditioner according to a sixth aspect includes the scroll compressor according to any one of the first to fifth aspects.

  Here, the leakage loss of the refrigerant in the scroll compressor can be reduced, which contributes to the improvement of the air conditioning capability.

  As described above, according to the present invention, the winding end portion of the wrap portion is formed in a reverse taper shape, and the winding intermediate portion of the wrap portion is formed in a reverse taper shape having a smaller taper ratio than the winding end portion. Accordingly, it becomes possible to cancel the combined change tendency of the gap due to the gas pressure inside the compression chamber during operation and the thermal expansion of the movable scroll, and to suppress the gap between the wrap portions from increasing, Leakage loss can be reduced.

It is a schematic block diagram of the air conditioning apparatus which employ | adopted the scroll compressor concerning one Embodiment of this invention. It is a schematic sectional drawing of the scroll compressor concerning one Embodiment of this invention. When the scroll structure concerning this invention is not employ | adopted, it is a figure which shows the state which the movable scroll deform | transformed convexly toward the stationary-side board part side by the thermal expansion at the time of a driving | operation. When the scroll structure concerning this invention is not employ | adopted, it is a figure which shows the change of the clearance gap between the lap | wrap parts by the gas pressure of the compression chamber inside at the time of a driving | operation, and the thermal expansion of a scroll. It is a figure which shows the movable scroll of the scroll structure concerning this invention. It is a figure which shows the fixed scroll of the scroll structure concerning this invention. It is a fragmentary sectional view which shows the scroll structure concerning this invention. It is a figure which shows the value of the taper ratio in the scroll structure concerning this invention. When the scroll structure concerning this invention is employ | adopted, it is a figure which shows the change of the clearance gap between the lap | wrap parts by the gas pressure of the compression chamber inside at the time of a driving | operation, and the thermal expansion of a scroll.

  DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment of a scroll compressor according to the present invention will be described with reference to the drawings. In addition, the specific structure of the scroll compressor concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) Configuration of Air Conditioner FIG. 1 is a schematic configuration diagram of an air conditioner 100 that employs a scroll compressor 1 according to an embodiment of the present invention.

  In the refrigerant circuit 101 of the air conditioner 100, the scroll compressor 1 that compresses the refrigerant, the radiator 102 that radiates the refrigerant, the expansion mechanism 103 that decompresses the refrigerant, and the evaporator 104 that evaporates the refrigerant are sequentially connected. It is constituted by. The refrigerant circuit 101 contains a refrigerant containing R32.

(2) Basic Configuration and Operation of Scroll Compressor FIG. 2 is a schematic sectional view of the scroll compressor 1 according to one embodiment of the present invention.

  The scroll compressor 1 has a vertically long cylindrical hermetic dome-shaped casing 10. The casing 10 is a pressure vessel composed of a casing body 11, an upper wall portion 12, and a bottom wall portion 13, and the inside thereof is hollow. The casing main body 11 is a cylindrical trunk having an axis extending in the vertical direction. The upper wall portion 12 is an airtightly welded and integrally joined to the upper end portion of the casing body 11 and is a bowl-shaped portion having a convex surface protruding upward. The bottom wall portion 13 is a bowl-shaped portion having a convex surface protruding downward, which is welded and integrally joined to the lower end portion of the casing body 11 in an airtight manner.

  The casing 10 accommodates a compression mechanism 14 that compresses the refrigerant and a motor 15 that is disposed below the compression mechanism 14. The compression mechanism 14 and the motor 15 are connected by a drive shaft 16 that is disposed so as to extend in the vertical direction in the casing 10.

  The compression mechanism 14 includes a housing 20, a fixed scroll 30 disposed in close contact with the housing 20, and a movable scroll 40 that meshes with the fixed scroll 30. The housing 20 is press-fitted and fixed to the casing body 11 over the entire outer circumferential surface in the circumferential direction. That is, the casing body 11 and the housing 20 are in close contact with each other in an airtight manner over the entire circumference. The inside of the casing 10 is a high-pressure space that is filled with a high-pressure refrigerant after being compressed by the compression mechanism 14, and the scroll compressor 1 is a so-called high-pressure dome type compressor. The housing 20 is formed with a housing recess 21 recessed in the center of the upper surface and a bearing portion 22 extending downward from the center of the lower surface. The housing 20 is formed with a bearing hole 23 that penetrates the lower end surface of the bearing portion 22 and the bottom surface of the housing recess 21, and the drive shaft 16 is rotatably fitted in the bearing hole 23 via the bearing 24. ing.

  A suction pipe 17 is inserted into the upper wall portion 12 of the casing 10 in an airtight manner so that a low-pressure refrigerant flows into the casing 10 from the outside to the compression mechanism 14. Further, a discharge pipe 18 that discharges the high-pressure refrigerant in the casing 10 to the outside of the casing 10 is fitted in the casing body 11 in an airtight manner. The suction pipe 17 penetrates the upper wall portion 12 of the casing 10 in the vertical direction, and an inner end portion is fitted into the fixed scroll 30 of the compression mechanism 14. The discharge pipe 18 penetrates the casing main body 11 of the casing 10 in the lateral direction, and the inner end communicates with the high-pressure space in the casing 10.

  The lower end surface of the fixed scroll 30 is in close contact with the upper end surface of the housing 20. The fixed scroll 30 is fixed to the housing 20 with bolts or the like.

  The fixed scroll 30 mainly has a fixed side plate portion 31 and a fixed side wrap portion 32. The fixed side wrap portion 32 is a spiral (involute) portion erected on one surface (here, the lower surface) of the fixed side plate portion 31. The movable scroll 40 mainly has a movable side plate portion 41 and a movable side wrap portion 42. The movable side wrap portion 42 is a spiral (involute) portion that meshes with the fixed side wrap portion 32 erected on one surface (here, the upper surface) of the movable side plate portion 41. In addition, the movable scroll 40 is supported by the housing 20 via the Oldham ring 49, and the upper end of the drive shaft 16 is fitted therein so that the inside of the housing 20 can revolve without rotating due to the rotation of the drive shaft 16. Yes. The other surface (here, the lower surface) of the movable side plate portion 41 of the movable scroll 40 is pressed against the fixed scroll 30 by a high-pressure refrigerant that fills the space between the movable side plate portion 41 and the housing recess 21. A compression chamber 39 is formed between the fixed scroll 30 and the movable scroll 40 by engaging the fixed side wrap portion 32 of the fixed scroll 30 and the movable side wrap 42 of the movable scroll 40 with each other. The compression chamber 39 is configured to compress the refrigerant by the volume between the lap portions 32 and 42 contracting toward the center as the movable scroll 40 turns.

  A discharge port 33 that communicates with the compression chamber 39 and an enlarged recess 34 that continues to the discharge port 33 are formed in the fixed side plate portion 31 of the fixed scroll 30. The discharge port 33 is a port for discharging the refrigerant after being compressed in the compression chamber 39, and is formed to extend in the vertical direction at the center of the fixed side plate portion 31. The enlarged recessed portion 34 is configured by a recessed portion that is recessed in the upper surface of the fixed side plate portion 31 and that extends in the horizontal direction. A chamber cover 35 is fixed to the upper surface of the fixed scroll 30 with a bolt or the like so as to close the enlarged recess 34. Then, the chamber cover 35 is covered with the enlarged concave portion 34, thereby forming a chamber chamber that is located above the discharge port 33 and into which the refrigerant flows from the compression chamber 39 through the discharge port 33. In addition, the fixed scroll 30 is formed with a suction port 36 through which the upper surface of the fixed scroll 30 and the compression chamber 39 communicate with each other and the suction pipe 17 is fitted. Further, the fixed scroll 30 and the housing 20 are formed with a communication channel (not shown) through which the refrigerant in the chamber chamber flows out into the high-pressure space.

  The motor 15 includes an annular stator 51 fixed to a wall surface in the casing 10, and a rotor 52 configured to be rotatable on the inner peripheral side of the stator 51. A winding is attached to the stator 51. The rotor 52 is drivably coupled to the movable scroll 40 of the compression mechanism 14 via a drive shaft 16 disposed at the axial center of the casing body 11 so as to extend in the vertical direction.

  In the lower space below the motor 15, lubricating oil is stored at the bottom, and a pump 60 is disposed. The pump 60 is fixed to the casing body 11 and attached to the lower end of the drive shaft 16 so as to pump up the stored lubricating oil. An oil supply passage 61 is formed in the drive shaft 16, and the lubricating oil pumped up by the pump 60 is supplied to each sliding portion through the oil supply passage 61.

  In the scroll compressor 1 having the basic configuration as described above, when the motor 15 is energized and driven, the rotor 52 rotates with respect to the stator 51, and thereby the drive shaft 16 rotates. When the drive shaft 16 rotates, an operation in which the movable scroll 40 turns with respect to the fixed scroll 30 is performed. As a result, the low-pressure refrigerant is sucked into the compression chamber 39 from the portion near the outer periphery of the compression chamber 39 (portion near the winding end of the wrap portions 32 and 42) through the suction pipe 17. The refrigerant sucked into the compression chamber 39 is compressed while being sent to a portion near the inner periphery of the compression chamber 39 (a portion near the winding start end of the wrap portions 32 and 42) as the volume of the compression chamber 39 changes. The high-pressure refrigerant compressed in the compression chamber 39 is sent to the high-pressure space in the casing 10 from the discharge port 33 at the center of the compression chamber 39 through the chamber chamber and the communication channel, and then through the discharge pipe 18. It is discharged out of the casing 10.

  During the operation of turning the movable scroll 40, the refrigerant pressure inside the compression chamber 39 formed by the fixed side wrap portion 32 and the movable side wrap portion 42 is changed between the fixed side wrap portion 32 and the movable side wrap portion 42. Therefore, the gap between the fixed side wrap portion 32 and the movable side wrap portion 42 is enlarged, and there is a possibility that the refrigerant leakage loss increases.

  Further, in the compression chamber 39, the refrigerant temperature increases from the winding end end (portion closer to the outer periphery) of the wrap portions 32 and 42 toward the winding start end (portion closer to the inner periphery). As a result, the fixed scroll 30 is deformed in a convex shape toward the root portion, and affects the gap between the fixed wrap portion 32 and the movable wrap portion 42. In particular, when a refrigerant such as R32 or the like whose discharge gas temperature tends to be high is used, the movable scroll 40 is fixed to the fixed side plate portion 31 ( Since it is greatly deformed in a convex shape toward the tooth root portion) side, the gap between the fixed side wrap portion 32 and the movable side wrap portion 42 is greatly affected.

  When the influence of the refrigerant pressure inside the compression chamber 39 during such operation and the influence of the thermal expansion of the scroll 40 overlap, the gap between the fixed side wrap part 32 and the movable side wrap part 42 becomes the lap part. As shown in FIG. 4, the spiral shape of the wrap portions 32, 42 is compared with the spiral start end side of the wrap portions 32, 42. A tendency to become larger at the winding end end side of the spiral shape appears. And the leakage loss of the refrigerant | coolant according to this tendency will generate | occur | produce.

  In FIGS. 3 and 4, for convenience of explanation, the amount of deformation due to thermal expansion and the degree of the gap between the fixed side wrap portion 32 and the movable side wrap portion 42 are shown considerably larger than actual.

  On the other hand, the scroll compressor 1 employs a scroll structure that takes into consideration the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40 as will be described later.

(3) Detailed structure of scroll and its characteristic Next, the detailed structure of the movable scroll 40 which considered the thermal expansion at the time of a driving | operation is demonstrated using FIGS. Here, FIG. 5 is a diagram showing a movable scroll 40 having a scroll structure according to the present invention. FIG. 6 is a diagram showing a fixed scroll 30 having a scroll structure according to the present invention. FIG. 7 is a partial cross-sectional view showing a scroll structure according to the present invention. FIG. 8 is a diagram showing the value of the taper ratio in the scroll structure according to the present invention. FIG. 9 is a diagram showing a change in the gap between the lap portions 32 and 42 due to the gas pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40 when the scroll structure according to the present invention is employed. 5 to 9, for the convenience of explanation, the degree of change in the taper ratio and the like are shown considerably larger than actual.

  As described above, when the influence of the refrigerant pressure inside the compression chamber 39 during operation and the influence of the thermal expansion of the scroll 40 overlap, the gap between the fixed side wrap part 32 and the movable side wrap part 42 becomes the lap part. 32 and 42 change in a complex manner from the winding start end to the winding end end of the spiral shape, and the spiral winding end end side of the wrap portions 32 and 42 compared to the spiral winding start end side of the wrap portions 32 and 42. The tendency to become large appears. More specifically, as shown in FIG. 4, the gap between the wrap portions 32, 42 is the refrigerant pressure inside the compression chamber 39 during operation on both the winding start end side and the winding end end side of the spiral shape. As a result, the distance between the fixed scroll 30 and the movable scroll 40 in the axial direction (vertical direction in the drawing) increases, and therefore, compared to when not operating (see the lap portion 42 indicated by the two-dot chain line in FIG. 4). During operation (refer to the lap portion 42 indicated by the solid line in FIG. 4), it is enlarged. However, since the movable scroll 40 is deformed in a convex shape toward the root portion of the fixed scroll 30 due to the thermal expansion of the movable scroll 40, the gap between the wrap portions 32 and 42 has a spiral shape with a large degree of deformation. There is a tendency that the spiral end end side (portion near the outer periphery) having a small degree of deformation becomes larger than the winding start end side (portion near the inner periphery).

  Therefore, here, as shown in FIGS. 5 to 8, in anticipation of a complex change tendency of the gap between the lap portions 32 and 42 due to the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the movable scroll 40. The winding end portions 32a and 42a of the wrap portions 32 and 42 are formed in a reverse taper shape, and the winding intermediate portions 32c and 42c of the wrap portions 32 and 42 are formed in a reverse taper shape having a smaller taper ratio than the winding end portions 32a and 42a. ing. Here, the winding end portions 32a and 42a are portions including the spiral end portion of the movable side wrap portion 42 and the fixed side wrap portion 32 (portions near the suction port 36 near the outer periphery). The winding start portions 32 b and 42 b are portions including the spiral winding start end of the movable side wrap portion 42 and the fixed side wrap portion 32 (portions near the discharge port 33 near the inner periphery). The winding intermediate portions 32c and 42c are portions between the winding start portions 32b and 42b and the winding end portions 32a and 42a. The reverse taper shape means a shape in which the tooth thickness of the tooth tip portion 38 is larger than the tooth thickness of the root portion 37 in the case of the fixed side wrap portion 32, and the root of the tooth in the case of the movable side wrap portion 42. It means a shape in which the tooth thickness of the tooth tip portion 48 is larger than the tooth thickness of the base portion 47. The taper ratio is a value obtained by subtracting the tooth thickness of the root portion 47 from the tooth thickness of the tooth tip portion 48 of the wrap portions 32 and 42 by the tooth thickness of the tooth tip portion 48.

  Thereby, as shown in FIG. 9, it becomes possible to cancel the complex change tendency of the gap due to the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40, and the wrap portion 32, It is possible to reduce the leakage loss of the refrigerant by suppressing an increase in the gap between 42. Specifically, as shown in FIG. 9, the fixed scroll is caused by the influence of the refrigerant pressure inside the compression chamber 39 during operation on both the winding start end side and the winding end end side of the spiral shape of the wrap portions 32 and 42. The distance in the axial direction (vertical direction in the drawing) between the moving scroll 30 and the movable scroll 40 is increased. Moreover, since the movable scroll 40 is deformed in a convex shape toward the root portion of the fixed scroll 30 due to the thermal expansion of the movable scroll 40, the movable scroll 40 and the fixed scroll 30 are movable on the winding end sides of the wrap portions 32 and 42. The axial distance from the scroll 40 is further increased. Such a tendency is the same as when the scroll structure according to the present invention is not employed (see FIG. 4). However, even if the axial interval between the fixed scroll 30 and the movable scroll 40 increases due to the refrigerant pressure inside the compression chamber 39 and the thermal expansion of the scroll 40 during operation, as shown in FIG. The side surfaces of the inversely tapered shapes 32 and 42 are brought close to each other. Thereby, it is suppressed that the clearance gap between the lap | wrap parts 32 and 42 becomes large. In addition, since the taper ratio is smaller on the winding start end side than the spiral winding end side of the wrap portions 32, 42, the degree of convex deformation due to the thermal expansion of the movable scroll 40 is the wrap portions 32, 32. This is because the different tendency is considered on the winding start end side than on the spiral winding end end side. And since the leakage loss of the refrigerant | coolant in the scroll compressor 1 can be reduced, it has contributed also to the improvement of an air-conditioning capability.

  Here, as shown in FIGS. 5 to 8, the reverse tapered shape at the winding end portions 32 a and 42 a of the wrap portions 32 and 42 has the maximum taper ratio.

  For this reason, here, the winding end portion 32a in which the gap between the wrap portions 32 and 42 may be maximized due to the combined change tendency of the gap due to the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40. 42a, the change tendency can be appropriately canceled out. Thereby, it can suppress that the clearance gap between the lap | wrap parts 32 and 42 in winding end part 32a and 42a becomes large, and can reduce the leakage loss of a refrigerant | coolant effectively.

  In addition, here, as shown in FIGS. 5 to 8, the winding start portions 32 b and 42 b of the wrap portions 32 and 42 have a tooth thickness of the root base portions 37 and 47 and a tooth thickness of the tooth tip portions 38 and 48. It has the same straight shape. Here, “straight shape” means that the taper ratio is zero (0).

  Therefore, here, the winding start portion 32b in which the gap between the wrap portions 32 and 42 may be minimized due to the combined change tendency of the gap due to the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40. 42b, the change tendency can be appropriately canceled to prevent the gap between the wrap portions 32, 42 at the winding start portions 32b, 42b from becoming large, and the leakage loss of the refrigerant can be effectively reduced. It is like that.

  In addition, here, as shown in FIGS. 5, 6, and 8, the reverse taper shape in the winding intermediate portions 32 c and 42 c of the wrap portions 32 and 42 is from the winding start portions 32 b and 42 b side to the winding end portions 32 a and 42 a. The taper ratio continuously changes to the side.

  For this reason, here, there is a possibility that the gap between the wrap portions 32 and 42 may change continuously due to the combined change tendency of the gap due to the refrigerant pressure inside the compression chamber 39 during operation and the thermal expansion of the scroll 40. In the portions 32c and 42c, the change tendency is appropriately canceled, and the gap between the wrap portions 32 and 42 in the winding intermediate portions 32c and 42c is suppressed from increasing, thereby effectively reducing the leakage loss of the refrigerant. Can be done.

  The present invention is widely applicable to a scroll compressor and an air conditioner including the scroll compressor.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 30 Fixed scroll 31 Fixed side board part 32 Fixed side wrap part 32a Winding end part 32b Winding start part 32c Winding intermediate part 37 Tooth root part 38 Tooth part 40 Movable scroll 41 Movable side board part 42 Movable side lap part 42a Winding End portion 42b Winding start portion 42c Winding intermediate portion 47 Tooth root portion 48 Tooth tip portion 100 Air conditioner

Japanese Patent Publication No. 63-15443

Claims (6)

A fixed scroll (30) in which a spiral fixed side wrap portion (32) is erected on one surface of the fixed side plate portion (31);
A movable scroll (40) is disposed so as to be pivotable facing the fixed scroll, and has a spiral movable side wrap portion (42) vertically engaged with the fixed side wrap portion on one surface of the movable side plate portion (41). )When,
With
Of the movable side wrap part and the fixed side wrap part, the winding end part (32a, 42a) which is a part including the spiral winding end is a tooth tip part than the tooth thickness of the root part (37, 47). (38, 48) has a large inverted taper tooth thickness,
A winding intermediate portion (32c, which is a portion between the winding start portion (32b, 42b) and the winding end portion which is a portion including a spiral winding start end of the movable side wrap portion and the fixed side wrap portion. 42c) has a reverse taper shape with a taper ratio smaller than that of the winding end portion,
Scroll compressor (1). The reverse taper shape at the end of winding has a maximum taper ratio,
The scroll compressor according to claim 1. The winding start portion has a straight shape in which the tooth thickness of the root portion and the tooth thickness of the tip portion are the same,
The scroll compressor according to claim 1 or 2. The reverse taper shape in the winding intermediate part has a taper ratio continuously changing from the winding start part side to the winding end part side,
The scroll compressor of any one of Claims 1-3. Used to compress refrigerant containing R32,
The scroll compressor of any one of Claims 1-4. A scroll compressor according to any one of claims 1 to 5,
An air conditioner (100) comprising:

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