JP2022108158A - Compressor, air conditioner, manufacturing method of compressor and manufacturing method of air conditioner - Google Patents

Abstract

To provide a compressor which is easy in manufacturing, and can enhance compression efficiency, an air conditioner, a manufacturing method of the compressor and a manufacturing method of the air conditioner.SOLUTION: A compressor 1A comprises: a first compression chamber component having a first inner wall face for defining a compression chamber for compressing a fluid, and a notch part for notching a corner part which is formed of the first inner wall face and a first end face located at an end part of the first inner wall face; a second compression chamber component having a mating face mating with the first end face, a second inner wall face for defining a compression chamber together with the first inner wall face, and a groove 62A formed between the second inner wall face and the mating face, and in a position in which an extension destination of the first inner wall face and the second inner wall face intersect with each other; and a slide member sliding in the compression chamber.SELECTED DRAWING: Figure 3

Description

The present disclosure relates to a compressor, an air conditioner, a method for manufacturing a compressor, and a method for manufacturing an air conditioner.

Some compressors are provided with a so-called relief portion in order to prevent interference with the inner wall of the compression chamber and improve the sliding efficiency of the piston.

For example, Patent Document 1 discloses a shaft having an eccentric portion that rotates, and a rolling piston that is inserted through the eccentric portion and revolves as the shaft rotates. A compressor is disclosed in which a concave relief portion is formed on the eccentric side of the shaft.

In the compressor disclosed in Patent Literature 1, a disc portion provided in the bearing is arranged in the direction of the revolution axis of the rolling piston. In this compressor, the relief portion is formed at the above location of the rolling piston, thereby reducing the sliding area of the rolling piston on the disk portion. As a result, energy efficiency is enhanced.

JP-A-2000-265979

On the other hand, in order to further improve the compression efficiency, it is conceivable to form a relief portion in the compression chamber in which the rolling piston revolves. This is because it is believed that by preventing interference between the compression chamber and other parts, the fluid can be more easily compressed, and the compression efficiency can be improved.

However, if the relief portion is large, the fluid will leak and the compression efficiency of the compressor will decrease. On the other hand, in order to make the relief portion smaller, it is necessary to form the relief portion using a cutting tool with a small tip angle, for example, and as a result, it is difficult to manufacture.

The present disclosure has been made to solve the above problems, and provides a compressor that can be easily manufactured and that can improve compression efficiency, an air conditioner, a method for manufacturing the compressor, and a method for manufacturing the air conditioner. for the purpose.

To achieve the above objectives, a compressor according to the present disclosure includes a first compression chamber component, a second compression chamber component, and a sliding member. The first compression chamber component has a first inner wall surface that defines a compression chamber that compresses fluid, and a notch that cuts out a corner portion formed by the first inner wall surface and a first end surface located at the end of the first inner wall surface. It has a notch. The second compression chamber component has a mating surface aligned with the first end surface, a second inner wall surface defining the compression chamber with the first inner wall surface, and a portion of the first inner wall surface between the second inner wall surface and the mating surface. a groove formed at a position where the extension and the second inner wall surface intersect. The sliding member slides in the compression chamber.

According to the configuration of the present disclosure, the first compression chamber component has a cutout portion that cuts out a corner portion formed by the first inner wall surface and the first end surface located at the end of the first inner wall surface, The second compression chamber component has a groove formed at a position where the extension of the first inner wall surface and the second inner wall surface intersect. Since the notches and grooves are formed in each part, it is easy to form small notches and grooves. As a result, it is easy to manufacture. In addition, small notches and grooves can be formed to suppress fluid leakage. As a result, the compression efficiency of the compressor can be enhanced.

Sectional view of a compressor according to Embodiment 1 of the present disclosure Cross-sectional view of the II-II cutting line shown in FIG. An enlarged cross-sectional view of a cylindrical portion and a bearing portion of a cylinder included in a compressor according to Embodiment 1 of the present disclosure Cross-sectional view of a cylindrical portion of a cylinder included in a compressor according to Embodiment 1 of the present disclosure Sectional view of a bearing portion of a cylinder included in a compressor according to Embodiment 1 of the present disclosure Flowchart of a method for manufacturing a compressor according to Embodiment 1 of the present disclosure Flowchart of method for manufacturing cylindrical portion or bearing portion of cylinder provided in compressor according to Embodiment 1 of the present disclosure A perspective view of a cylinder included in a compressor according to Embodiment 2 of the present disclosure when viewed from below A perspective view of a cylindrical portion of a cylinder included in a compressor according to Embodiment 2 of the present disclosure, as viewed from above. A perspective view of a bearing portion of a cylinder included in a compressor according to Embodiment 2 of the present disclosure when viewed from above A perspective view of a scroll body included in a compressor according to Embodiment 3 of the present disclosure FIG. 11 is an enlarged cross-sectional view of the base of the scroll body when the scroll body is cut along the XII-XII cutting line shown in FIG. 11; Block diagram of an air conditioner according to Embodiment 4 of the present disclosure A perspective view of a modified example of a cylindrical portion of a cylinder included in a compressor according to Embodiment 2 of the present disclosure A perspective view of another modification of the cylindrical portion of the cylinder included in the compressor according to Embodiment 2 of the present disclosure A perspective view of still another modification of the cylindrical portion of the cylinder included in the compressor according to Embodiment 2 of the present disclosure A perspective view of a modified example of a bearing portion of a cylinder included in a compressor according to Embodiment 2 of the present disclosure FIG. 11 is a perspective view of another modified example of the bearing portion of the cylinder included in the compressor according to Embodiment 2 of the present disclosure FIG. 11 is a perspective view of still another modified example of the bearing portion of the cylinder included in the compressor according to the second embodiment of the present disclosure;

Hereinafter, a compressor, an air conditioner, a method for manufacturing a compressor, and a method for manufacturing an air conditioner according to embodiments of the present disclosure will be described in detail with reference to the drawings. In addition, the same code|symbol is attached|subjected to the same or equivalent part in the figure. In the orthogonal coordinate system XYZ shown in the figure, the Y-axis is the advance and retreat direction of the vanes provided in the compressor, the Z-axis is the revolution axis direction of the rolling piston provided in the compressor, and the X-axis is the direction perpendicular to the Y-axis and the Z-axis. . Hereinafter, description will be made with reference to this coordinate system as appropriate.

(Embodiment 1)
The compressor according to Embodiment 1 is a rotary compressor in which a relief portion is provided on the inner wall of the cylinder in order to improve the fit between the rolling piston and the cylinder and improve the compression ratio. In this compressor, in order to facilitate the formation of the relief portion, grooves, recesses, etc. are provided in the parts forming the compression chamber, and the relief portion is formed by combining these parts.
First, the configuration of the rotary compressor will be described with reference to FIGS. 1 and 2. FIG.

In addition, the escape part is a structure such as a dent or groove formed in a part, or a clearance provided between a part and another part, in order to prevent the part from interfering with other parts. .

FIG. 1 is a cross-sectional view of a compressor 1A according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view taken along the line II--II shown in FIG. In addition, in FIG. 1, the boundary between the integrated cylindrical portion 11A and the bearing portion 12A of the cylinder 10A is indicated by a dotted line for easy understanding.

As shown in FIG. 1, the compressor 1A includes a cylinder 10A, a bearing 20 arranged below the cylinder 10A, a shaft 30 rotatably held by a bearing portion 12A, and a rolling shaft attached to the shaft 30. a piston 40; Furthermore, as shown in FIG. 2, the compressor 1A includes a vane 50 that contacts the rolling piston 40 and partitions the inside of the cylinder 10A.

The cylinder 10A is a member that forms a compression chamber that compresses fluid. Furthermore, the cylinder 10A also serves as a member that holds the shaft 30 passing through the compression chamber. Therefore, as shown in FIG. 1, the cylinder 10A has a shape in which the cylindrical portion 11A and the bearing portion 12A are integrated.

The cylindrical portion 11A has a circular hole 111 at its center that functions as a compression chamber that accommodates and compresses fluid. The cylindrical portion 11A is arranged with the axis L1 of the hole 111 directed in the vertical direction.

Further, as shown in FIG. 2, the cylindrical portion 11A is formed with a vane groove 112 and a suction port 113 penetrating in the radial direction. The vane 50 is inserted into the vane groove 112, and the vane 50 advances and retreats. On the other hand, the suction port 113 is connected to a suction pipe (not shown) through which fluid flows, and guides the fluid into the hole 111 . On the other hand, as shown in FIG. 1, a bearing portion 12A is arranged on the cylindrical portion 11A. The bearing portion 12A is integral with the cylindrical portion 11A.

The bearing portion 12A has a shape in which a small cylindrical portion 122 is connected to the center and top of a disc portion 121 . The disc portion 121 is formed to have the same diameter as the cylindrical portion 11A. The disc portion 121 covers the hole 111 of the cylindrical portion 11A on the cylindrical portion 11A to close the hole 111. As shown in FIG. On the other hand, the small cylindrical portion 122 is formed with a through hole 126 for passing the shaft 30 therethrough. The through hole 126 also penetrates the disk portion 121 . It is arranged coaxially with the axis L1 of the hole 111 . Furthermore, the shaft 30 is loosely inserted in the through hole 126 . Thus, the bearing portion 12A holds the shaft 30 slidably.
In the present embodiment, the disc portion 121 has the same diameter as the cylindrical portion 11A, but the disc portion 121 may have an outer diameter smaller than the outer diameter of the cylindrical portion 11A, or conversely larger than the outer diameter of the cylindrical portion 11A. It may be the outer diameter.

On the other hand, below the cylindrical portion 11A of the cylinder 10A, as shown in FIG. 1, a bearing 20 having the same function as the bearing portion 12A is arranged in order to allow the shaft 30 to pass through the hole 111. As shown in FIG.

The bearing 20 is formed in a disc shape with a diameter larger than that of the hole 111 . The bearing 20 closes the hole 111 from below the cylinder 10A. A through hole 21 is also formed in the bearing 20 coaxially with the axis L1 of the hole 111, and the shaft 30 is loosely inserted into the through hole 21. As shown in FIG. Thereby, the bearing 20 also slidably holds the shaft 30 .

Since the shaft 30 is held by the small cylindrical portion 122 of the bearing portion 12A and the bearing 20, it extends in the direction of the axis L1 as shown in FIG. The shaft 30 is connected to a motor (not shown) and driven by the motor to rotate. Further, the shaft 30 has an eccentric portion 31 inside the hole 111 of the cylindrical portion 11A, as shown in FIG. A rolling piston 40 is attached to the eccentric portion 31 . Shaft 30 moves rolling piston 40 by rotating.

The rolling piston 40 is cylindrically shaped as shown in FIGS. The above-described eccentric portion 31 is inserted into the cylinder. The rolling piston 40 and the eccentric portion 31 are positioned inside the hole 111 of the cylindrical portion 11A. In this state, the outer peripheral surface of rolling piston 40 is close to inner wall surface 110 of hole 111 . The rolling piston 40 swings about the axis L1 when the shaft 30 is rotated by a motor (not shown). In other words, the rolling piston 40 rotates around the axis L1 while being eccentric with respect to the axis L1. On the other hand, as shown in FIG. 2, the tip of the vane 50 is in contact with the rolling piston 40 .

The vane 50 is formed in the shape of a quadrangular prism whose tip is rounded in an R shape. Although not shown, the vane 50 has the same height as the length in the direction of the axis L1 of the cylindrical portion 11A of the cylinder 10A, that is, the height in the Z direction. Its tip is in contact with the rolling piston 40 as described above. Thereby, the vane 50 partitions the space between the rolling piston 40 and the inner wall surface 110 of the hole 111 . Also, although not shown, the vane 50 is biased against the rolling piston 40 by a spring provided in the vane groove 112 . Thereby, the vane 50 partitions the space regardless of the operation of the rolling piston 40 .

A discharge port 123 is provided on the opposite side of the vane 50 in the rotational direction R of the rolling piston 40, as shown in FIG. The discharge port 123 is formed in a disk portion 121 that closes the upper end of the hole 111 of the cylindrical portion 11A. On the other hand, the suction port 113 described above is arranged on the side of the vane 50 in the rotation direction R of the rolling piston 40 .

In this positional relationship, when the rolling piston 40 rotates in the rotational direction R from a state eccentric to the upper region inside the hole 111, the rolling piston 40 returns to a state eccentric to the upper region inside the hole 111 again. , the volume of the space S1 on the suction port 113 side of the vane 50 increases as it rotates. As a result, the fluid is sucked into the space S1 through the suction port 113 . At the same time, the volume of the space S2 on the discharge port 123 side of the vane 50 decreases as the rolling piston 40 rotates. As a result, the fluid inside the space S2 on the discharge port 123 side is compressed. Then, a valve (not shown) of the discharge port 123 is opened and the compressed fluid is discharged from the discharge port 123 .

Thus, the rolling piston 40 rotates about the axis L1 inside the bore 111 of the cylinder 10A to compress the fluid in the bore 111 .

At this time, the outer peripheral surface of the rolling piston 40 and the inner wall surface 110 of the hole 111 are close to each other as described above. The fluid compressed inside the space S2 on the port 123 side may leak into the space S1 on the suction port 113 side of the vane 50, resulting in a decrease in compression efficiency.

Therefore, in order to keep the rolling piston 40 as close as possible to the inner wall surface 110 of the compressor 1A, the gap generated between the rolling piston 40 and the inner wall surface 110 of the hole 111 is set to 0.5 at maximum. It is assembled in a state of 1 mm. In the compressor 1A, the compression efficiency is enhanced by manufacturing and assembling each part such as the rolling piston 40 and the cylinder 10A with high accuracy.

However, as shown in FIG. 1, the cylinder 10A has an interior angle A1. Specifically, the inner wall surface 110 of the hole 111 of the cylindrical portion 11A and the inner wall surface 124 of the disk portion 121 of the bearing portion 12A form an internal angle A1. Therefore, even if the rolling piston 40 and the cylinder 10A are manufactured with high precision, there is a possibility that the inner angle A1 and the corner portion of the rolling piston 40 interfere with each other. As a result, the sliding efficiency of the rolling piston 40 may decrease. Also, the rolling piston 40 and the cylinder 10A may be damaged and the fluid may leak.

Therefore, although not shown in FIGS. 1 and 2, in the compressor 1A, a relief portion is formed at the interior angle A1 of the cylinder 10A. Next, referring to FIGS. 3 to 5, the relief portion of the cylinder 10A will be described.

FIG. 3 is an enlarged sectional view of the cylindrical portion 11A and the bearing portion 12A of the cylinder 10A. FIG. 4 is a cross-sectional view of the cylindrical portion 11A. FIG. 5 is a cross-sectional view of the bearing portion 12A. In addition, FIG. 3 expands the left part of the cross section of the cylinder 10A shown in FIG. In addition, in FIG. 3, the sizes of the relief portion 60A and the gap C1 are emphasized for easy understanding. 4 and 5 also emphasize the size of the chamfer 61A and the groove 62A, albeit to a lesser degree than in FIG.

As shown in FIG. 3, a relief portion 60A is formed at an internal angle A1 formed by the cylindrical portion 11A and the bearing portion 12A of the cylinder 10A.

Specifically, the extension of the inner wall surface 110 of the cylindrical portion 11A and the extension of the inner wall surface 124 of the bearing portion 12A intersect to form an interior angle A1, and the apex 63 of the interior angle A1 is A relief portion 60A is formed by scraping off a location where the intersection of the extension of the inner wall surface 110 and the extension of the inner wall surface 124 is located.

In the escape portion 60A, the gap C1 between the rolling piston 40 and the inner wall surface 110 is 0.1 mm at maximum. The width W2 on the side of the rolling piston 40 is formed to be 0.01 mm or more and 0.1 mm or less. Further, of the height H1 of the relief portion 60A, the height H2 on the rolling piston 40 side of the vertex portion 63 of the interior angle A1 is formed to have the same size as the width W2.

In order to form such a small relief portion 60A by machining, it is necessary to use a tool with a small point angle, such as a cutting tool or an end mill. In this case, the cutting edge of the tool may resonate and the machined surface may undulate or rattle. As a result, productivity is low and manufacturing is difficult.

Therefore, in the compressor 1A, the relief portion 60A is formed by combining a chamfered portion 61A formed in the cylindrical portion 11A of the cylinder 10A and a groove 62A formed in the bearing portion 12A. That is, in the compressor 1A, the cylindrical portion 11A and the bearing portion 12A of the cylinder 10A are separately manufactured, and in the manufacturing process, the chamfered portion 61A and the groove 62A are formed, and the cylindrical portion with the chamfered portion 61A is formed. By combining 11A and a bearing portion 12A in which a groove 62A is formed, the chamfered portion 61A and the groove 62A are combined to form a relief portion 60A.
The cylindrical portion 11A and the bearing portion 12A are also referred to as compression chamber components because they are components that form the compression chamber of the cylinder 10A.

As shown in FIG. 4, the chamfered portion 61A is formed at a corner portion 115 formed by the inner wall surface 110 of the cylindrical portion 11A and the upper surface 114 of the cylindrical portion 11A. Its shape is obtained by cutting the corner portion 115 along a plane inclined with respect to the inner wall surface 110 . For example, the chamfered portion 61A is a C-chamfered surface cut at an angle of 45° with respect to the inner wall surface 110, that is, a so-called angular surface. The width W3 of the chamfered portion 61A is 0.01 mm or more and 0.1 mm or less, which is the same as the height H2 described above. The chamfered portion 61A extends along the inner circumference of the cylindrical portion 11A while maintaining its shape. As a result, the chamfered portion 61A is formed over the entire inner circumference of the cylindrical portion 11A.

On the other hand, the groove 62A is formed in the lower surface of the disk portion 121 of the bearing portion 12A, that is, the inner wall surface 124, as shown in FIG. The cross-sectional shape of the groove is semicircular. The radius R1 is the same as the width W3 and the height H2 of the chamfered portion 61A. The groove 62A draws a circle centered on the axis L12 of the disk portion 121 while maintaining the cross-sectional shape of the groove. That is, the groove 62A draws a circular track. The radius R12 of the circle drawn by the groove 62A is the same as the radius R11 of the inner circumference of the cylindrical portion 11A having the chamfered portion 61A shown in FIG.

In addition, the portion of the escape portion 60A shown in FIG. , is not a portion that prevents interference with the rolling piston 40 . Therefore, the width W3 of the chamfered portion 61A may be smaller or larger than the size described above. The radius R1 of the cross-sectional shape of the groove 62A may be smaller or larger than the size mentioned above as long as the size of the width W2 mentioned above is maintained.

Returning to FIG. 1, the cylindrical portion 11A and the bearing portion 12A of the cylinder 10A are combined in a stacked state in this order from below. An upper surface 114 of the cylindrical portion 11A shown in FIG. 4 is fitted and joined to an annular portion 125 outside the groove 62A on the lower surface of the disk portion 121 shown in FIG.

At this time, the axis L11 of the cylindrical portion 11A shown in FIG. 4 and the axis L12 of the disk portion 121 of the bearing portion 12A shown in FIG. As described above, the radius R11 of the inner circumference of the cylindrical portion 11A in which the chamfered portion 61A is formed and the radius R12 of the circle drawn by the groove 62A are the same. Therefore, when the cylindrical portion 11A and the bearing portion 12A are combined, the apex portion of the corner portion 115 formed with the chamfered portion 61A shown in FIG. matches. As a result, as shown in FIG. 3, the chamfered portion 61A and the groove 62A are positioned outside or above the vertex portion 63 of the interior angle A1. Accordingly, even if the corner portion 41 of the rolling piston 40 is positioned at the vertex portion 63 of the interior angle A1, the corner portion of the rolling piston 40 does not interfere with the cylindrical portion 11A and the bearing portion 12A. This prevents the sliding efficiency of the rolling piston 40 from deteriorating.

Also, the chamfered portion 61A is formed at the upper end of the inner wall surface 110 of the cylindrical portion 11A. Furthermore, the groove 62A is formed in the inner wall surface 124 of the disk portion 121 of the bearing portion 12A. Since the chamfered portion 61A and the groove 62A are formed at the outer corner portion or on a flat surface, it is easy to manufacture. As a result, productivity is enhanced when manufacturing the relief portion 60A. Moreover, the manufacture of the escape portion 60A is facilitated. Next, a method for manufacturing the compressor 1A will be described with reference to FIGS. 6 and 7. FIG.

FIG. 6 is a flow chart of a method for manufacturing the compressor 1A. FIG. 7 is a flowchart of a method for manufacturing the cylindrical portion 11A or the bearing portion 12A of the cylinder 10A included in the compressor 1A.

First, as shown in FIG. 6, the cylindrical portion 11A and the bearing portion 12A are produced (step S1). In these productions, the cylindrical portion 11A and the bearing portion 12A, which are sintered bodies, are produced using a sintering method in which compacted powder is pressurized and heated to produce a sintered body.

Specifically, as shown in FIG. 7, first, raw material powder, for example, raw material powder of iron and steel containing iron as a main component is prepared (step S11). When using a plurality of types of raw material powders, prepared raw material powders are mixed. For example, when using a binder, a lubricant, etc., the raw material powder is mixed with the binder and the lubricant.

Subsequently, the raw material powder is molded by filling the prepared raw material powder into the mold for molding the cylindrical portion 11A and pressing the filled raw material powder (step S12). In this molding, a mold having a mold for the cylindrical portion 11A having the chamfered portion 61A described above is used. Then, the raw material powder is pressurized with a pressure of 500 to 800 MPa. Thereby, a molded body having the shape of the cylindrical portion 11A having the chamfered portion 61A is produced.

Next, the compact is sintered by heating at a temperature lower than the melting point of the raw material powder while the compact is pressed (step S13). In the sintering of this compact, for example, when the raw material powder is iron, it is heated at 1000 to 1300° C., which is lower than the melting point of iron. When the compact is heated at such a temperature while being pressurized, the particles of the raw material powder are bonded together and metallurgically bonded. Then, a sintered body is completed.

Through the above steps, the cylindrical portion 11A, which is a sintered body and has the chamfered portion 61A, is produced. Similarly, the mold in step S12 is changed to a mold for molding the bearing portion 12A, and steps S11 to S13 are carried out to produce the sintered bearing portion 12A. In manufacturing the bearing portion 12A, a mold having a shape of the bearing portion 12A having the groove 62A is used. As a result, the bearing portion 12A having the groove 62A is produced.

Returning to FIG. 6, when the cylindrical portion 11A and the bearing portion 12A are produced, the produced cylindrical portion 11A and the bearing portion 12A are combined (step S2). At this time, the upper surface 114 of the cylindrical portion 11A shown in FIG. 4 is aligned with the annular portion 125 outside the groove 62A of the disk portion 121 of the bearing portion 12A shown in FIG. As a result, the chamfered portion 61A is adjacent to the groove 62A shown in FIG. As a result, a space escape portion 60A in which the groove 62A and the chamfered portion 61A are integrated is formed.

Returning to FIG. 6, the combined cylindrical portion 11A and bearing portion 12A are heated to join them together. Thereby, the cylindrical portion 11A and the bearing portion 12A are joined (step S3). In this joining, the cylindrical portion 11A and the bearing portion 12A are heated while being pressed against each other, that is, in a pressurized state. This increases the bonding strength. The heating temperature is preferably lower than the melting points of the materials of the cylindrical portion 11A and the bearing portion 12A, similarly to the heating in step S13. Thereby, sintering may be advanced to advance densification of the sintered body.

In addition, in this joining, the cylindrical portion 11A and the bearing portion 12A are heated and sintered in the same manner as in the sintering of the compact in step S13. Since they are the same sintering, the sintering in step S13 is called primary sintering, and this heating is called secondary sintering.

After joining the cylindrical portion 11A and the bearing portion 12A, the surface shapes of the cylindrical portion 11A and the bearing portion 12A are modified by machining (step S4).

Specifically, in order to improve assembly accuracy when assembled into the compressor 1A, or to improve the adhesion of the rolling piston 40, the inner wall surface 110 of the cylindrical portion 11A and the bearing portion 12A shown in FIG. The inner wall surface 124 of the plate portion 121 is subjected to machining such as cutting and polishing. This corrects the surface shape. For example, processing is performed to increase the flatness of the inner wall surface 124 of the disk portion 121 or to increase the roundness of the inner wall surface 110 of the cylindrical portion 11A. In addition, processing is performed to increase the degree of orthogonality between the inner wall surface 124 and the inner wall surface 110 . In addition, in this machining, the processing up to the removal of the relief portion 60A formed in step S2 is not performed, and only the surface shape is corrected. This leaves the relief portion 60A after machining.

The cylinder 10A is produced by the above steps S1-S4. Then, the compressor 1A is assembled using the produced cylinder 10A (step S5). That is, the components for the compressor 1A, such as the bearing 20, the shaft 30, the rolling piston 40, the vane 50, etc., are assembled to the manufactured cylinder 10A in the arrangement described above to assemble the compressor 1A. Compressor 1A is completed by the above.

Note that the chamfered portion 61A described above is an example of the notch portion referred to in this specification. Also, the cylindrical portion 11A and the bearing portion 12A are examples of the first compression chamber component and the second compression chamber component. In addition, the inner wall surface 110 and the upper surface 114 of the cylindrical portion 11A are examples of a first inner wall surface and a first end surface positioned at the end of the first inner wall surface. The annular portion 125 and the inner wall surface 124 of the disk portion 121 of the bearing portion 12A outside the groove 62A are an example of a mating surface and a second inner wall surface. The rolling piston 40 is an example of a sliding member.

Further, the step of correcting the surface shape of the cylindrical portion 11A and the bearing portion 12A in step S4 described above is an example of the step of arranging the surface shape referred to in this specification, and the step of assembling the compressor 1A in step S5 is , which is an example of a process of assembling a piston into a compression chamber.

As described above, in the compressor 1A according to Embodiment 1, the cylindrical portion 11A, which is a part of the cylinder 10A, is positioned at the corner portion 115 formed by the inner wall surface 110 and the upper surface 114 at the upper end portion of the inner wall surface 110. It has a chamfered portion 61A provided. Also, the bearing portion 12A of the component of the cylinder 10A has a groove 62A provided in the inner wall surface 124 thereof. By combining the cylindrical portion 11A and the bearing portion 12A with the groove 62A positioned at the extension of the inner wall surface 110, the chamfered portion 61A and the groove 62A form a relief portion 60A. Since the chamfered portion 61A and the groove 62A are formed in the cylindrical portion 11A and the bearing portion 12A, respectively, and the cylindrical portion 11A and the bearing portion 12A are combined, the compressor 1A having the relief portion 60A can be easily manufactured.

Further, since only the chamfered portion 61A and the groove 62A are formed in the cylindrical portion 11A and the bearing portion 12A, respectively, the corner portion 115 of the cylindrical portion 11A is cut to form the chamfered portion 61A, and the bearing portion 12A is formed with the chamfered portion 61A. Since the groove 62A is only carved in the inner wall surface 124, it is easy to form the minute chamfered portion 61A and the groove 62A. As a result, even a very small escape portion 60A can be easily manufactured.

Furthermore, in the compressor 1A, since it is easy to form the minute relief portion 60A, it is possible to form the minute relief portion 60A to suppress fluid leakage from the compression chamber. As a result, the compression efficiency of the compressor 1A can be improved.

In the compressor 1A, the cylindrical portion 11A and the bearing portion 12A are each produced by a sintering method. At this time, since the chamfered portion 61A and the groove 62A can be formed simultaneously with the production of the cylindrical portion 11A and the bearing portion 12A by the sintering method, the production efficiency is high. In particular, the production efficiency is high compared to the case where the chamfered portion 61A and the groove 62A are formed by machining.

(Modification)
In Embodiment 1, the cylindrical portion 11A and the bearing portion 12A are sintered bodies, but the cylindrical portion 11A and the bearing portion 12A are not limited to this. For example, the cylindrical portion 11A and the bearing portion 12A may be made of a bulk body. In that case, the bulk body may be steel produced by casting.

Here, in this specification, the term "bulk body" refers to a body in which the material is more integrated than the sintered body described above, and which is in the form of a mass as a whole. For example, it refers to a mass produced by casting. A sintered body generally has open pores and closed pores, but a bulk body does not have these open pores and closed pores.

Moreover, in Embodiment 1, the cylindrical portion 11A and the bearing portion 12A are made of a steel material containing iron as a main component, but the material of the cylindrical portion 11A and the bearing portion 12A is not limited to this. For example, the material of the cylindrical portion 11A and the bearing portion 12A may be a metal material other than steel, such as an aluminum alloy or a titanium alloy. Moreover, a resin material may be used. Even with such materials, the cylindrical portion 11A and the bearing portion 12A can be produced by a sintering method.

Furthermore, in Embodiment 1, the cylindrical portion 11A and the bearing portion 12A are produced by a sintering method, but the method for producing the cylindrical portion 11A and the bearing portion 12A is not limited to this. For example, the cylindrical portion 11A and the bearing portion 12A may be produced by machining such as cutting and grinding. Alternatively, it may be produced by casting. In either case, the chamfered portion 61A and the groove 62A are formed when the cylindrical portion 11A and the bearing portion 12A themselves are manufactured. This is because after the cylindrical portion 11A and the bearing portion 12A are assembled and joined together, the relief portion 60A has a complicated shape and is difficult to manufacture.

In Embodiment 1, the cylindrical portion 11A and the bearing portion 12A are joined by heating after combining the cylindrical portion 11A and the bearing portion 12A. However, the method of joining the cylindrical portion 11A and the bearing portion 12A is not limited to this. For example, the method of joining the cylindrical portion 11A and the bearing portion 12A may be mechanical joining such as bolts and rivets, or metallurgical joining such as welding and brazing. Diffusion bonding may also be used. Alternatively, the cylindrical portion 11A and the bearing portion 12A may be joined by adhesion.

(Embodiment 2)
In Embodiment 1, the escape portion 60A is formed at the boundary between the cylindrical portion 11A of the cylinder 10A and the bearing portion 12A. However, the position of the escape portion 60A is not limited to this. In the compressor 1A, the relief portion 60A may be provided at the boundary formed by the inner wall surfaces 110, 124 defining the compression chambers and another inner wall surface, or at the boundary formed between the other inner wall surfaces.

In compressor 1B according to Embodiment 2, relief portion 60B is provided in vane groove 112 . Hereinafter, a compressor 1B according to Embodiment 2 will be described with reference to FIGS. 8 to 10. FIG. In addition, in Embodiment 2, a configuration different from that in Embodiment 1 will be described.

FIG. 8 is a perspective view of a cylinder 10B included in a compressor 1B according to Embodiment 2 as viewed from below. FIG. 9 is a perspective view when the cylindrical portion 11B of the cylinder 10B is viewed from above. FIG. 10 is a perspective view when the bearing portion 12B of the cylinder 10B is viewed from above.

8 and 9, the suction port 113 is omitted to simplify the shape of the cylindrical portion 11B for easy understanding. Also, the shape of the vane groove 112 is simplified to a linear shape to emphasize its size. 8 and 10, the through hole of the bearing portion 12B for passing the shaft 30 is omitted to simplify the shape of the bearing portion 12B.

As shown in FIG. 8, the cylinder 10B provided in the compressor 1B has not only a relief portion 60A formed in the cylindrical portion 11B, but also a relief portion 60B is provided in the vane groove 112 as well.

The relief portion 60B is formed by combining two chamfered portions 61B formed in the cylindrical portion 11B shown in FIG. 9 and two grooves 62B formed in the bearing portion 12B shown in FIG.

As shown in FIG. 9, two chamfers 61B are formed at the upper ends of the side walls 116 and 117 of the vane groove 112, ie, at the +Z ends. The cross-sectional shape of the groove is the same as that of the chamfered portion 61A described in the first embodiment. The chamfered portion 61B extends toward the inside of the cylindrical portion 11B while maintaining the shape of the cross section of the groove. It extends to the inner wall surface 110 of the cylindrical portion 11B. Furthermore, the chamfered portion 61B is connected to the chamfered portion 61A described in the first embodiment.

On the other hand, two grooves 62B are formed in the inner wall surface 124 on the -Z side of the bearing portion 12B, as shown in FIG. The two grooves 62B are parallel to each other and extend from the end of the bearing portion 12B toward the axis L12. The distance D1 from the groove cross-sectional center to the groove cross-sectional center of these grooves 62B is the same as the distance D2 from the side wall 116 to the side wall 117 of the vane groove 112 shown in FIG. The two grooves 62B shown in FIG. 10 are connected to the circularly extending groove 62A described in the first embodiment.

Although not shown, the two grooves 62B face the two chamfered portions 61B shown in FIG. 9 by joining the cylindrical portion 11B to the bearing portion 12B as in the first embodiment. The position of the chamfered portion 61B with respect to the grooves 62B is the same as the position of the chamfered portion 61A with respect to the groove 62A described in the first embodiment with reference to FIG. As a result, the two grooves 62B form two relief portions 60B together with the two chamfered portions 61B by joining the cylindrical portion 11B to the bearing portion 12B.

As described in Embodiment 1, the vane 50 that advances and retreats in the vane groove 112 has a quadrangular prism shape with rounded ends, and the corners of the prism may be sharp. However, as shown in FIG. 8, a relief portion 60B is formed at the boundary between the side wall 116 of the vane groove 112 and the inner wall surface 124 . Therefore, even if the corners of the quadrangular prism of the vane 50 are sharp, they are less likely to interfere with the vane grooves 112 .

In addition, the vane groove 112 is closed by the disk portion 121 shown in FIG. 1 of the bearing portion 12B when the cylindrical portion 11B is joined to the bearing portion 12B. The disk portion 121 is an example of the plate-like portion referred to in this specification. Also, the vane 50 is an example of a sliding member. Furthermore, the cylindrical portion 11B and the bearing portion 12B are examples of the first compression chamber component and the second compression chamber component. Side walls 116 and 117 of vane groove 112 are an example of a first inner wall surface. The chamfered portion 61B is an example of a notch portion.

As described above, in the compressor 1B according to Embodiment 2, the vane groove 112 is provided with the relief portion 60B. For this reason, even in the vane groove 112, a minute relief portion 60B can be formed to suppress fluid leakage from the vane groove 112. FIG. Moreover, the slidability of the vane 50 in the vane groove 112 can be improved.

In the second embodiment, similarly to the first embodiment, the chamfered portion 61B and the groove 62B are formed in the cylindrical portion 11B and the bearing portion 12B, respectively, and the escape portion 60B is formed only by combining the cylindrical portion 11B and the bearing portion 12B. to form This eliminates the need for complicated machining and facilitates the manufacture of the compressor 1B.

(Embodiment 3)
In Embodiments 1 and 2, the compressors 1A and 1B are rotary compressors, but the compressors 1A and 1B are not limited to this. The present disclosure is widely applicable to compressors in general. The present disclosure is applicable to, for example, screw compressors and scroll compressors.

A compressor 1C according to Embodiment 3 is a scroll compressor. Hereinafter, a compressor 1C according to Embodiment 3 will be described with reference to FIGS. 11 and 12. FIG. In addition, in Embodiment 3, a configuration different from Embodiments 1 and 2 will be described.

FIG. 11 is a perspective view of scroll body 70 included in compressor 1C according to the third embodiment. FIG. 12 is an enlarged cross-sectional view of a portion of the base of the scroll body 70 when the scroll body 70 is cut along the XII-XII section line shown in FIG.

As shown in FIG. 11, the scroll body 70 provided in the compressor 1C includes a spiral tooth 71, a support 72 that supports the spiral tooth 71, and a relief provided near the joint between the spiral tooth 71 and the support 72. and a portion 60C.

The two scroll bodies 70 compress the fluid between the spiral teeth 71 by swinging one of the scroll bodies 70 with respect to the other while the spiral teeth 71 of the two scroll bodies 70 are meshed with each other. In order to produce such action, the spiral tooth 71 has a shape in which a plate is spirally bent. A support 72 is provided at the end of the plate of the spiral tooth 71 in the direction in which the axis L71 extends, that is, at the base of the spiral tooth 71 .

The support body 72 is formed in a disk shape, and spiral teeth 71 are arranged on the plate surface side thereof. The plate surface of the support 72 is perpendicular to the side wall surface of the spiral tooth 71 . As a result, as shown in FIG. 12, the plate surface of the support 72 and the side wall surface of the spiral tooth 71 form a right internal angle A2. Therefore, when the scroll body 70 meshes with another scroll body (not shown) and the spiral teeth 71, there is a possibility that the tips of the spiral teeth of the other scroll body (not shown) interfere with the inner angle A2. Therefore, in order to prevent interference, the scroll body 70 is provided with a relief portion 60C.

The relief portion 60C is formed by combining a chamfered portion 61C formed at the base-side end portion of the spiral tooth 71 and a groove 62C formed in the plate surface portion of the support 72 . The chamfered portion 61C has the same chamfered cross-sectional shape as the chamfered portion 61A described in the first embodiment. Therefore, description thereof is omitted. Further, the groove 62C has the same groove cross-sectional shape as the groove 62A described in the first embodiment. Therefore, description thereof is omitted.

The chamfered portions 61C are formed on both side surfaces of the end face of the plate on the base side of the spiral tooth 71 . Although not shown, it is formed over the entire plate of the spiral tooth 71 .

On the other hand, although not shown, the groove 62C extends spirally so as to be arranged along the plate of the spiral tooth 71 when the spiral tooth 71 is joined to the support 72 . Two spiral grooves 62C are formed in order to follow each side of the spiral tooth 71 plate. Thus, when the spiral tooth 71 is joined to the support 72, the chamfered portion 61C and the groove 62C face each other to form a space. As a result, the chamfered portion 61C and the groove 62C form a relief portion 60C. As a result, when the scroll body 70 engages another scroll body (not shown) with the spiral teeth 71, the tips of the spiral teeth 71 are less likely to interfere with each other.

The spiral tooth 71 described above is an example of the first compression chamber component and the scroll-like component referred to in this specification. Also, the support 72 is an example of the second compression chamber component and the disk-shaped component. Another scroll body (not shown) that meshes with the scroll body 70 is an example of a sliding member. The plate surface of the plate of the spiral tooth 71 is an example of the first inner wall surface, and the end surface of the plate of the spiral tooth 71 is an example of the first end surface. The chamfered portion 61C is an example of a notch portion.

As described above, in the compressor 1C according to Embodiment 3, the relief portion 60C is provided at the base portion of the spiral tooth 71 of the scroll body 70 . Therefore, even in a scroll compressor including the scroll body 70, it is possible to form a minute escape portion 60C and suppress fluid leakage. As a result, compression efficiency can be improved.

In the scroll body 70 as well, as in the first and second embodiments, the relief portion 60C is formed by forming the chamfered portion 61C and the groove 62C in separate parts. is easy.

(Embodiment 4)
Compressors 1A-1C according to embodiments 1-3 may be used in air conditioners. Embodiment 4 is an air conditioner 2 provided with these compressors 1A.

An air conditioner according to Embodiment 4 will be described below with reference to FIG. 13 . In the fourth embodiment, the description will focus on the configuration different from the first to third embodiments.

FIG. 13 is a block diagram of the air conditioner 2 according to Embodiment 4. As shown in FIG.

As shown in FIG. 13, the air conditioner 2 includes a compressor 1A, a fan 3 and a heat exchanger 4. The compressor 1A, the fan 3, and the heat exchanger 4 are incorporated in the housing 7 of the outdoor unit together with the accumulator 5, the four-way valve 6, and other parts.

Compressor 1A is connected to heat exchanger 4, accumulator 5 and four-way valve 6 to form a refrigerant circuit for circulating refrigerant.

Meanwhile, the fan 3 blows air to the heat exchanger 4 . The heat exchanger 4 exchanges heat between the refrigerant in the refrigerant circuit and the blown air. As a result, the air conditioner 2 performs air conditioning.

For the air conditioner 2, various parts such as a compressor 1A, a fan 3, a heat exchanger 4, an accumulator 5, and a four-way valve 6 are prepared to form a refrigerant circuit and assembled to the housing 7 of the outdoor unit. Manufactured by

As described above, the air conditioner 2 according to the fourth embodiment includes the compressor 1A according to the first embodiment. Therefore, the air conditioner 2 has high refrigerant compression efficiency, and as a result, high cooling and heating performance.

The compressors 1A-1C, the air conditioner 2, the method of manufacturing the compressor, and the method of manufacturing the air conditioner 2 according to Embodiments 1-3 of the present disclosure have been described above. The air conditioner 2, the method for manufacturing the compressor, and the method for manufacturing the air conditioner 2 are not limited to these.

For example, in the compressors 1A-1C according to Embodiments 1-3, the chamfered portions 61A-61C are so-called C-chamfered, but the shape of the chamfered portions 61A-61C is not limited to this. The chamfered portions 61A to 61C may have any shape as long as they are provided at the corners formed by the inner wall surface 110 of the compression chamber and the end surface located at the end of the inner wall surface 110 .

14A and 14B are perspective views of modifications of the cylindrical portion 11B of the cylinder 10B included in the compressor 1B according to Embodiment 2. FIG. 14A and 14B, the shape of the cylindrical portion 11B is simplified and the size of the vane groove 112 is emphasized for easy understanding.

As shown in FIG. 14A, the chamfered surfaces of the chamfered portions 61A and 61B may be steeper than the C-chamfered surface. Although not shown, the chamfered surfaces of the chamfered portions 61A and 61B may have a gentler slope than the C-chamfered surface. In other words, so-called scalene chamfering may be used.

As shown in FIG. 14B, the chamfered portions 61A and 61B may be R-chamfered. That is, chamfering of a round surface may be used.

In this manner, the chamfered portions 61A-61C only need to have surfaces formed by scraping off the corner portions.

Further, in the compressors 1A-1C according to Embodiments 1-3, the compressors 1A-1C include the chamfered portions 61A-61C described above, but the compressors 1A-1C are not limited to this. The cylindrical portions 11A and 11B and the spiral teeth 71 included in the compressors 1A-1C are examples of the first compression chamber parts referred to in this specification. In the compressors 1A-1C, the first compression chamber parts It is only required that the first inner wall surface defining the compression chamber for compressing the fluid and the first end surface located at the end of the first inner wall surface form a notch portion that cuts out the corner portion.

Here, the notch portion does not mean a portion produced by a manufacturing method of cutting and removing, but is formed at a corner portion formed by the first inner wall surface and the first end surface, and the corner portion It is a dent that has the shape of a cutout.

Therefore, the chamfers 61A-61C may be replaced with notches.
FIG. 14C is a perspective view of still another modification of the cylindrical portion 11B of the cylinder 10B included in the compressor 1B according to Embodiment 2. FIG. Note that in FIG. 14C, the shape of the cylindrical portion 11B is simplified and the size of the vane groove 112 is emphasized in order to facilitate understanding, as in FIGS. 14A and 14B.

As shown in FIG. 14C, the chamfered portions 61A and 61B may be replaced with notched portions having a shape obtained by cutting out stepped corner portions. That is, the chamfered portions 61A and 61B are regarded as a kind of chamfering in the construction field, and may be replaced with a notch portion called a chamfered surface.

The chamfered portions 61A and 61B having the shapes described with reference to FIGS. 14A, 14B, and 9 and the notched portion shown in FIG. 14C may be provided in the compressors 1A to 1C in a mixed state.

Further, in the compressors 1A-1C according to Embodiments 1-3, the grooves 62A-62C are semicircular in groove cross section, but the shape of the grooves 62A-62C is not limited to this. If the grooves 62A-62C are formed at the location where the apex 63 of the inner angle A1 formed by the extension of the inner wall surface 110 of the compression chamber and the inner wall surface 124 forming the compression chamber together with the inner wall surface 110 is located. good. In other words, the grooves 62A-62C may be formed at the intersections of the extension of the inner wall surface 110 and the inner wall surface 124. As shown in FIG. Therefore, as far as this is concerned, its shape is arbitrary.

15A to 15C are perspective views of modifications of the bearing portion 12B of the cylinder 10B provided in the compressor 1B according to the second embodiment. 15A to 15C, the shape of the bearing portion 12B is simplified by omitting the through-hole of the bearing portion 12B through which the shaft 30 is passed, in order to facilitate understanding.

As shown in FIG. 15A, the grooves 62A and 62B may have a rectangular cross-sectional shape. Also, as shown in FIG. 15B, the grooves 62A and 62B may be triangular, ie, wedge-shaped or V-shaped, pointed toward the bottom of the groove. Further, as shown in FIG. 15C, in cross-sectional view of the groove, the side of the right triangle having the right angle may be positioned on the side of the groove opening, and the oblique side may face the opposite side of the groove opening.

Note that the grooves 62A and 62B having the shapes described with reference to FIGS. 15A to 15C and 10 may be mixedly arranged in the compressors 1A to 1C.

In Embodiment 4, compressor 1A is used in the outdoor unit of air conditioner 2, but compressors 1B and 1C according to Embodiments 2 and 3 may be applied to air conditioners. Further, the compressors 1A-1C can be applied not only to the air conditioner 2 but also to refrigerators and freezers. Thus, the compressors 1A-1C are applicable to refrigeration cycle equipment.

1A, 1B, 1C compressor 2 air conditioner 3 fan 4 heat exchanger 5 accumulator 6 four-way valve 7 housing 10A, 10B cylinder 11A, 11B cylindrical portion 12A, 12B bearing portion 20 Bearing 21 Through hole 30 Shaft 31 Eccentric part 40 Rolling piston 41 Corner part 50 Vane 60A, 60B, 60C Relief part 61A, 61B, 61C Chamfered part 62A, 62B, 62C Groove 63 Vertex part , 64 center, 70 scroll body, 71 spiral tooth, 72 support body, 110 inner wall surface, 111 hole, 112 vane groove, 113 suction port, 114 upper surface, 115 corner portion, 116, 117 side wall, 121 disc portion, 122 small Cylindrical portion 123 Discharge port 124 Inner wall surface 125 Annular portion 126 Through hole L1, L11, L12, L71 Axis line A1, A2 Interior angle C1 Gap D1, D2 Distance H1, H2 Height R Direction of rotation , R1, R11, R12 radius, S1, S2 space, W1, W2, W3 width.

Claims (14)

a first inner wall surface defining a compression chamber for compressing a fluid; and
a cutout portion that cuts out a corner portion formed by the first inner wall surface and a first end surface located at the end of the first inner wall surface;
a first compression chamber component having
a mating surface aligned with the first end surface;
a second inner wall surface defining the compression chamber together with the first inner wall surface; and
A groove formed between the second inner wall surface and the mating surface and at a position where the extension of the first inner wall surface and the second inner wall surface intersect,
a second compression chamber component having
a sliding member that slides in the compression chamber;
Compressor with At least one of the first compression chamber component and the second compression chamber component is a sintered body in which a large number of powders are bonded together,
A compressor according to claim 1 . At least one of the first compression chamber component and the second compression chamber component is a single massive bulk body as a whole,
A compressor according to claim 1 . The first compression chamber component and the second compression chamber component are made of a metal material or a resin material,
A compressor according to any one of claims 1 to 3. The first end surface and the mating surface are bonded by diffusion bonding,
A compressor according to any one of claims 1 to 4. The first compression chamber component is a cylindrical cylinder with the first inner wall surface being a cylindrical inner peripheral surface, the first end surface being a cylindrical end surface, and the cylindrical end surface side being open,
The second compression chamber component closes the opening on the side of the cylindrical end surface, arranges the second inner wall surface on the inner surface thereof, and extends in a circular shape at the boundary with the inner peripheral surface of the cylinder. A bearing having a disk portion in which a groove is arranged,
A compressor according to any one of claims 1 to 5. the first compression chamber component is a cylindrical cylinder having an open cylindrical end and radially extending vane grooves at the cylindrical end in which vanes are slidable;
The second compression chamber component closes the vane groove from the cylindrical end side, is arranged with the second inner wall surface facing the vane groove, and is located at the boundary with the inner wall of the vane groove. A bearing having a plate-shaped portion that extends in the direction in which the vane groove extends and arranges the groove along the inner wall of the vane groove,
A compressor according to any one of claims 1 to 6. The first compression chamber component is a scroll-shaped component wound with a plate having a plate surface as the first inner wall surface and an end surface as the first end surface,
The second compression chamber component is a disk-shaped component in which the second inner wall surface is a plate surface facing the end surface of the plate,
said first compression chamber part and said second compression chamber part forming a scroll body of said compressor;
A compressor according to any one of claims 1 to 5. A compressor according to any one of claims 1 to 8;
a fan for blowing air,
a heat exchanger that exchanges heat between the refrigerant compressed by the compressor and the air blown by the fan;
air conditioner. A first inner wall surface for demarcating a compression chamber for compressing a fluid, and a notch portion for notching a corner portion formed by the first inner wall surface and a first end surface located at the end of the first inner wall surface. fabricating a first compression chamber component having
a mating surface for mating with the first end surface, a second inner wall surface adjacent to the mating surface and defining the compression chamber, and a groove formed between the mating surface and the second inner wall surface, fabricating a second compression chamber component having
The manufactured first compression chamber component and the manufactured second compression chamber component are in a state in which the mating surface is aligned with the first end surface, and the groove is arranged in an extension of the first inner wall surface. a step of combining with
a step of joining the first compression chamber component and the second compression chamber component after combining the first compression chamber component and the second compression chamber component;
assembling a sliding member into a compression chamber formed by joining the first compression chamber component and the second compression chamber component;
A method of manufacturing a compressor comprising: 11. The method according to claim 10, further comprising the step of machining at least one of the first inner wall surface and the second inner wall surface to adjust the surface shape after joining the first compression chamber component and the second compression chamber component. A method of manufacturing the described compressor. In the step of producing the first compression chamber part and the step of producing the second compression chamber part, the first compression chamber part and the fabricating a second compression chamber component;
A method for manufacturing a compressor according to claim 10 or 11. In the step of joining the first compression chamber component and the second compression chamber component, the first compression chamber component and the second compression chamber component are diffusion-bonded.
A method for manufacturing a compressor according to any one of claims 10 to 12. A method for manufacturing a compressor according to any one of claims 10 to 13;
combining the manufactured compressor, fan and heat exchanger;
A method for manufacturing an air conditioner comprising:

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