JP5466027B2 - 2-cylinder rotary compressor - Google Patents

Description

  The present invention relates to a two-cylinder rotary compressor having two cylinders in a compression mechanism section.

  Generally, in a conventional two-cylinder rotary compressor, the compression mechanism section includes two cylinders having compression chambers, two eccentric parts, a crankshaft that is connected to a power source and rotates, and a crankshaft. By passing either one of the two eccentric parts from the hole through which the shaft and the eccentric part can pass, the annular partition plate disposed between the two eccentric parts and the crankshaft are pivotally supported. However, the two cylinders are sealed together with the annular surface of the partition plate, and are constituted by two cylinder heads constituting a compression chamber and a rolling piston that is mounted on an eccentric portion and rotates in each cylinder. As the eccentric portion rotates in the cylinder, the refrigerant sucked into the cylinder is compressed (for example, Patent Document 1).

JP 2009-180203 A (3rd page, FIG. 3)

  In the conventional compressor, as shown in FIG. 18 and FIG. 19 in the configuration diagram of the conventional compressor, in the assembly process, the shaft and the eccentric part of the crankshaft can pass in order to place the partition plate between the cylinders. A hole is required for the partition plate, and the inner diameter φd1 of the hole needs to be slightly larger than the outer diameter φD1 of the eccentric portion through which the hole passes. For this reason, there is a gap that is not sealed between the inner peripheral surface of the partition plate inserted between both cylinders and the outer peripheral surface of the crankshaft facing the partition plate. As a result of the gap L between the refrigerants, the refrigerant in both the compression chambers flows into the gap, resulting in a problem that the compressibility of the refrigerant is reduced. In order to solve such a problem, in a conventional compressor, a rolling piston is mounted on an eccentric part, and the edge of the hole in the partition plate and a part of the end surface of the rolling piston are overlapped to form a seal. The leakage of the compressed refrigerant from the compression chamber of each cylinder to the gap was prevented. However, in this method, if the amount of eccentricity of the eccentric portion is increased in order to increase the compression ratio, the hole of the partition plate must also be increased, so that the gap between the hole of the partition plate and the outer peripheral surface of the rolling piston is again. There was a problem that the gap L occurred and the compression rate was lowered. On the other hand, in Patent Document 1, as shown in FIGS. 20 and 21, one outer diameter φD2 ′ of the eccentric portion is made smaller than the outer diameter φD2 of the other eccentric portion, and the inner diameter φd2 ′ of the hole of the partition plate is set. Shows a configuration that reduces the gap and reduces the leakage of the compressed refrigerant from the compression chamber to the gap by reducing the diameter to approximately the same size as φD2 and increasing the outer diameter of the rolling piston attached to one eccentric part. Yes. However, cutting the outer peripheral surface of the eccentric portion inward from the outer peripheral surface of the crankshaft causes strength problems, and reducing the eccentric portion is equivalent to reducing the amplitude of the eccentric portion. There was a limit to improving the displacement.

  The present invention was made to solve the above-described problems, eliminates the gap between the inner peripheral surface of the hole provided in the partition plate and the outer peripheral surface of the crankshaft, and An object of the present invention is to provide a two-cylinder rotary compressor having a configuration capable of improving the compression ratio by preventing compression leakage without reducing the outer diameter of the eccentric portion.

The two-cylinder rotary compressor of the present invention is
In a two-cylinder rotary compressor having a crankshaft that is rotated by external power,
The compression mechanism is
A cylindrical first cylinder;
A cylindrical second cylinder arranged coaxially with the first cylindrical cylinder;
A first eccentric portion provided integrally with the crankshaft and rotating along the inner peripheral surface of the first cylinder;
A second eccentric portion provided integrally with the crankshaft and rotating along the inner peripheral surface of the second cylinder;
Between the first eccentric part and the second eccentric part, the first eccentric part, the second eccentric part, and the crankshaft are provided integrally, and have the same rotation axis as the crankshaft, and the first eccentric part And a disk part for partitioning between the second eccentric part,
An outer peripheral surface of the disk part and an annular partition plate fitted to the first eccentric part ;
A first cylinder head fixed to the first cylinder, sealing an opening surface of the first cylinder facing the partition plate, and supporting the crankshaft;
A second cylinder head that is fixed to the second cylinder and seals the opening surface of the second cylinder facing the disk portion and the partition plate , and supports the crankshaft;
The first cylinder head is hermetically sealed by the inner wall surface of the first cylinder head, the outer peripheral surface of the first eccentric part, the surface of the partition plate facing the first cylinder head, and the inner peripheral surface of the first cylinder. A compression chamber;
Sealed by the inner wall surface of the second cylinder head, the outer circumferential surface of the second eccentric portion, the disk portion and the partition plate facing the second cylinder head, and the inner circumferential surface of the second cylinder. A second compression chamber;
It is characterized by forming.

The compression mechanism of this 2-cylinder rotary compressor is
A cylindrical first cylinder;
A cylindrical second cylinder arranged coaxially with the first cylindrical cylinder;
A first eccentric portion provided integrally with the crankshaft and rotating along the inner peripheral surface of the first cylinder;
A second eccentric portion provided integrally with the crankshaft and rotating along the inner peripheral surface of the second cylinder;
Between the first eccentric part and the second eccentric part, the first eccentric part, the second eccentric part, and the crankshaft are provided integrally, and have the same rotation axis as the crankshaft, and the first eccentric part And a disk part for partitioning between the second eccentric part,
An outer peripheral surface of the disk part and an annular partition plate fitted to the first eccentric part ;
A first cylinder head fixed to the first cylinder, sealing an opening surface of the first cylinder facing the partition plate, and supporting the crankshaft;
A second cylinder head that is fixed to the second cylinder and seals the opening surface of the second cylinder facing the disk portion and the partition plate , and supports the crankshaft;
The first cylinder head is hermetically sealed by the inner wall surface of the first cylinder head, the outer peripheral surface of the first eccentric part, the surface of the partition plate facing the first cylinder head, and the inner peripheral surface of the first cylinder. A compression chamber;
Sealed by the inner wall surface of the second cylinder head, the outer circumferential surface of the second eccentric portion, the disk portion and the partition plate facing the second cylinder head, and the inner circumferential surface of the second cylinder. A second compression chamber;
Because it is characterized by forming
As a result of eliminating the gap existing between both cylinders of the conventional two-cylinder rotary compressor and preventing compression leakage from the compression chamber without reducing the eccentric amount of the eccentric portion. Can be improved.

It is a block diagram of the compression mechanism part in Embodiment 1 of the 2-cylinder rotary compressor concerning this invention. It is a partial exploded perspective view of the compression mechanism part in Embodiment 1 of the 2-cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part in Embodiment 2 of the 2 cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part in Embodiment 3 of the 2 cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is sectional drawing and bottom view which show the partition plate in Embodiment 4 of the 2-cylinder rotary compressor concerning this invention. It is sectional drawing of the crankshaft in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention, and the crankshaft periphery. It is a disassembled perspective view which shows the compression mechanism part of the compressor in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is a disassembled perspective sectional view which shows the compression mechanism part of the compressor in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is a perspective view which shows the crankshaft, the 1st eccentric part, and disk part in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is the front view and top view which show the crankshaft, the 1st eccentric part, and disk part in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is a perspective view which shows the partition plate in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is a perspective view which shows the attachment state of the crankshaft, the 1st eccentric part, a disk part, a partition plate, and a guide in Embodiment 4 of the 2 cylinder rotary compressor concerning this invention. It is a perspective sectional view showing the attachment state of the crankshaft, the 1st eccentric part, the disk part, the partition plate, and the guide in Embodiment 4 of the 2 cylinder rotary compressor concerning the present invention. It is a block diagram of the compression mechanism part in Embodiment 5 of the 2 cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part in Embodiment 6 of the 2 cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part in Embodiment 7 of 2 cylinder rotary compressor concerning this invention. It is a block diagram of the compression mechanism part of the conventional 2 cylinder rotary compressor. It is sectional drawing of the crankshaft in the conventional 2 cylinder rotary compressor, and the crankshaft periphery. 2 is a configuration diagram of a compression mechanism portion of a two-cylinder rotary compressor of Patent Document 1. FIG. 2 is a cross-sectional view of a crankshaft and a portion around the crankshaft in a two-cylinder rotary compressor of Patent Document 1. FIG.

Embodiment 1 FIG.
Embodiment 1 of the present invention will be described below with reference to the drawings. FIG. 1 is a configuration diagram of a compression mechanism unit 100 of a two-cylinder rotary compressor according to Embodiment 1 of the present invention.
The crankshaft 101, the first and second eccentric portions 102a and 102b, and the disc portion 104, which are pivotally supported by the first and second cylinder heads 109a and 109b and connected to a drive unit (not shown), are made of a material such as metal. It is integrally formed by cutting or the like. The first and second eccentric parts 102a and 102b have a phase difference of 180 degrees and are integrally formed with the disk part 104 so as to sandwich the disk part 104 therebetween. A rolling piston 103 is rotatably mounted on the outer peripheral surfaces of the first and second eccentric portions 102a and 102b. A guide 106 having an inner peripheral surface that slide-fits with the disc portion 104 is disposed on the outer peripheral surface of the disc portion 104, and cylindrical first and second cylinders are provided on both sides of the disc portion 104 and the guide 106. 107a and 107b are arranged. The first and second cylinders 107a and 107b, the guide 106, and the first and second cylinder heads 109a and 109b that support the crankshaft are fastened by bolts or the like, so that the first and second cylinders are fastened. Sealed first and second compression chambers 108a and 108b are formed in 107a and 107b.

  The configuration of the internal space of each compression chamber will be described. The first compression chamber 108a includes an inner wall surface of the first cylinder head 109a, an outer peripheral surface of the rolling piston 103 rotatably mounted on the first eccentric portion 102a, and a first cylinder head 109a of the disc portion 104. And the inner peripheral surface of the first cylinder 107a. The second compression chamber 108b includes an inner peripheral surface of the second cylinder 107b, an inner wall surface of the second cylinder head 109b, and an outer peripheral surface of the rolling piston 103 rotatably mounted on the second eccentric portion 102b. The disk portion 104 is sealed by the disk surface facing the second cylinder head 109b and the inner peripheral surface of the second cylinder 107b. Further, the diameter of the disk portion 104 is made larger than the inner diameters of the first and second cylinders 107a and 107b, and the peripheral end portion is sandwiched between the first and second cylinders 107a and 107b. In addition, a sliding fitting portion of the disc portion 104, the guide 106, and the first and second cylinders 107a and 107b is formed as a labyrinth structure.

  Here, the internal mechanism of the first and second compression chambers 108a and 108b will be described with reference to the drawings. FIG. 2 is a partially exploded perspective view of the compression mechanism unit 100. Here, only the lower second compression chamber 108b will be described. A groove is cut in the axial direction of the second cylinder 107b constituting the inner wall surface of the compression chamber 108b in the axial direction of the cylinder, and is attached to the groove by a spring or gas pressure. A biased vane 110 is provided. Further, on both sides of the vane 110, there are provided an inlet for sucking refrigerant from the outside and an outlet for sending compressed refrigerant (not shown) to the outside. Since the vane 110 always abuts against the rolling piston 103 by energization, the low-pressure refrigerant and the high-pressure refrigerant in the second compression chamber 108b can be shut off. A similar internal mechanism is configured in the first compression chamber 108a.

  Next, the refrigerant compression process in the compression mechanism unit 100 will be described. The refrigerant that has flowed into the first and second compression chambers 108a and 108b partitioned by the vane 110 has a rolling piston 103 rotatably mounted on the outer periphery of the first and second eccentric portions 102a and 102b. The first and second compression chambers 108a and 108b are compressed by one rotation along the inner wall surfaces of the first and second compression chambers 108a and 108b. The refrigerant thus compressed is discharged from the discharge port to the outside of the compression chamber.

  When the compression mechanism unit 100 is configured in this manner, the disk portion 104 is provided integrally with the first and second eccentric portions 102a and 102b and the crankshaft, and thus either of the first and second eccentric portions 102a and 102b. There is no need to provide a hole in the disk portion 104 for penetrating the hole. As a result, it is possible to eliminate the gap that has conventionally existed between the inner peripheral surface of the hole provided between the partition plates and the outer peripheral surface of the crankshaft. Further, since the first and second compression chambers 108a and 108b are always sealed by the disk portion 104, it is possible to prevent compression leakage from the first and second compression chambers 108a and 108b. Further, since the disk portion 104 is integrally formed with the crankshaft 101 without depending on the outer diameter of the first and second eccentric portions 102a and 102b, the eccentricity of the first and second eccentric portions 102a and 102b is determined. It is possible to increase the amount. Furthermore, since the sliding fitting part of the disk part 104, the guide 106, and the first and second cylinders 107a and 107b is formed as a labyrinth structure, the sealing property of the sliding fitting part can be improved.

  Thus, without reducing the amount of eccentricity of the eccentric portion, the gap existing between both cylinders of the conventional two-cylinder rotary compressor can be eliminated, and compression leakage from the compression chamber can be prevented. As a result, it is possible to provide a two-cylinder rotary compressor capable of improving the compression rate.

Embodiment 2. FIG.
Hereinafter, the second embodiment of the present invention will be described based on the drawings, with a focus on differences from the first embodiment. FIG. 3 is a configuration diagram of the compression mechanism unit 200 of the two-cylinder rotary compressor according to the second embodiment of the present invention.
The compression mechanism 200 differs from the compression mechanism 100 shown in FIG. 1 in that the guide 206 and the first and second cylinders 107a and 107b have the same inner diameter. The second difference is that the disk portion 204 has substantially the same outer diameter as the inner diameters of the first and second cylinders 107a and 107b. With this configuration, although not shown, the first and second cylinders 107a and 107b and the guide 206 can also be configured as integrally molded parts.

  Since the internal mechanism and the compression process of the first and second compression chambers 108a and 108b are the same as those in the first embodiment, they are omitted.

  As described above, the outer diameter of the guide 206 and the inner diameters of the first and second cylinders 107a and 107b have the same diameter, and the disk portion 204 is substantially the same as the inner diameter of the first and second cylinders 107a and 107b. Even if the configuration has an outer diameter, a predetermined object can be achieved. In addition, since the first and second cylinders 107a and 107b and the guide 206 can be configured as integrally molded parts, productivity can be improved.

Embodiment 3 FIG.
In the following, the third embodiment of the present invention will be described based on the drawings, with a focus on differences from the second embodiment. FIG. 4 is a configuration diagram of the compression mechanism unit 300 of the two-cylinder rotary compressor according to Embodiment 3 of the present invention.
The first difference between the compression mechanism 300 and the compression mechanism 200 shown in FIG. 3 is that the compression mechanism 300 is fitted on the outer peripheral surface of a disc 304 provided integrally with the crankshaft 301 and the first and second eccentric parts 102a and 102b. An annular partition plate 305 is provided. The second difference is that the first compression chamber 308a includes an inner wall surface of the first cylinder head 109a, an outer peripheral surface of the rolling piston 103 attached to the first eccentric portion 102a, a disk portion 304, and a partition plate 305. The first cylinder head 109a is sealed by the board surface facing the first cylinder head 109a and the inner peripheral surface of the first cylinder 107a. The third difference is that the second compression chamber 308b includes an inner wall surface of the second cylinder head 109b, an outer peripheral surface of the rolling piston 103 attached to the second eccentric portion 102b, a disk portion 304, and a partition plate 305. The second cylinder head 109b is sealed by the board surface facing the second cylinder head 109b and the inner peripheral surface of the second cylinder 107b. The fourth difference is that the partition plate 305 fitted to the disk portion 304 has a diameter larger than the inner diameter of the first and second cylinders 107a and 107b, and the guide 106 and the first and second cylinders 107a and 107b. It is a point which forms a labyrinth structure with 107b.

  Since the internal mechanism and compression process of the first and second compression chambers 308a and 308b are the same as those in the second embodiment, a description thereof will be omitted.

  Note that the partition plate 305 may be press-fitted, welded, or bonded to the disk portion 304.

  Thus, even if the first and second cylinders 107a and 107b are partitioned by the disk portion 304 and the partition plate 305, the intended purpose can be achieved. Further, the diameter of the disk portion 304 can be reduced, and as a result, the maximum diameter of the crankshaft 301 is reduced. For this reason, the processing time at the time of manufacturing a crankshaft can be shortened, and the quantity of the metal material required for manufacture can also be reduced. As a result, the production cost of the crankshaft 401 can be reduced.

Embodiment 4 FIG.
Hereinafter, the fourth embodiment of the present invention will be described based on the drawings, with a focus on differences from the third embodiment. FIG. 5 is a configuration diagram of the compression mechanism 400 of the two-cylinder rotary compressor according to Embodiment 4 of the present invention. FIG. 6 is a sectional view and a bottom view showing the partition plate 405. 7 is a cross-sectional view and a plan view of the crankshaft 401, the first eccentric portion 402a, the disc portion 404, the partition plate 405, and the rolling piston 103. FIG. Differences between the compression mechanism 400 and the compression mechanism 300 shown in FIG. 4 will be described with reference to FIGS. The first difference is that the circular partition plate 405 has a counterbore-shaped circular recess into which the disk portion 404 is fitted, and further, as shown in FIG. The point is that a through hole for fitting the end of the eccentric portion 402a is provided. The second difference is that the axial direction of the crankshaft 401 of the first eccentric part 402a provided integrally with the crankshaft 401 is larger on the disk part 404 side than the height of the first cylinder. Is a point. A third difference is that the partition plate 405 is fitted with the first eccentric portion 402a to form a double fitting structure. The fourth difference is that the rolling piston 103 attached to the first eccentric portion 402a is in contact with the panel surface of the double-fitted partition plate 405 on the first eccentric portion 402a side. is there. The difference in the fifth, the first compression chamber 408a is an inner wall surface of the first cylinder head 109a, and the outer circumferential surface of the rolling piston 103 rotatably mounted on the first eccentric portion 402a, specifications Setsuban It is a point sealed by the board surface which faces the 1st cylinder head 109a of 405, and the internal peripheral surface of the 1st cylinder 107a.

  Here, the detail of the partition plate 405 is demonstrated using figures. FIG. 8 is an exploded perspective view of the compression mechanism 400 according to Embodiment 4 of the present invention. FIG. 9 is an exploded perspective sectional view of the compression mechanism unit 400. FIG. 10 is a perspective view of the crankshaft 401, the first eccentric portion 402a, and the disc portion 404. FIG. FIG. 11 is a front view and a plan view of the crankshaft 401, the first eccentric portion 402a, and the disc portion 404. FIG. 12 is a perspective view of the partition plate 405. FIG. 13 is a perspective view showing an attachment state of the crankshaft 401, the first eccentric portion 402a, the disc portion 404, the partition plate 405, and the guide 106. FIG. FIG. 14 is a perspective cross-sectional view showing a state in which the crankshaft 401, the first eccentric portion 402a, the disc portion 404, the partition plate 405, and the guide 106 are attached. Here, it demonstrates especially using FIG. By fitting the concave portion of the partition plate 405 with the disk portion 404, the partition plate 405 is accurately positioned with respect to the disk portion 404. Furthermore, as a result of fitting in the first eccentric portion 402a and the through hole provided in the recess, the positioning is accurately performed with respect to the first eccentric portion 402a. In this manner, a double fitting structure of the partition plate 405, the disk portion 404, and the first eccentric portion 402a is formed. Although not illustrated, the second eccentric portion 102b may be configured to protrude from the partition plate 405, and a double fitting structure including the partition plate 405, the second eccentric portion 102b, and the disk portion 404 may be employed.

  Since the internal mechanism and compression process of the first and second compression chambers 408a and 308b are the same as those in the third embodiment, a description thereof will be omitted.

  Thus, even if the eccentric portion 402a, the disc portion 404, and the partition plate 405 form a double fitting structure, the intended purpose can be achieved. Further, by adopting the double fitting structure, the partition plate 405 can be accurately positioned with respect to the eccentric portion 402a and the disc portion 404. In addition, since the processing accuracy of the through hole can be set within a range that can absorb the processing error, it is possible to further improve the productivity. Furthermore, since the outer diameter of the disc portion 404 and the axial thickness of the crankshaft can be reduced, the production cost of the crankshaft 401 can be further reduced.

Embodiment 5 FIG.
Hereinafter, the fifth embodiment of the present invention will be described based on the drawings, with a focus on differences from the fourth embodiment. FIG. 15 is a configuration diagram of the compression mechanism 500 of the two-cylinder rotary compressor according to the fifth embodiment of the present invention.
The compression mechanism 500 is different from the compression mechanism 400 shown in FIG. 5 in that the inner diameters of the guide 206 and the first and second cylinders 107a and 107b are the same. The second difference is that the partition plate 505 that forms a double fit with the disk portion 404 and the protruding portion of the first eccentric portion 402a is substantially the same as the inner diameter of the first and second cylinders 107a and 107b. It is a point having a diameter. With this configuration, although not shown, the first and second cylinders 107a and 107b and the guide 206 can also be configured as integrally molded parts.

  Details of the first and second compression chambers 408a and 308b and details of the compression process are the same as those in the fourth embodiment, and a description thereof will be omitted.

  Thus, the outer diameter of the guide 206 and the inner diameters of the first and second cylinders 107a and 107b have the same diameter, and the partition plate 505 is substantially the same as the inner diameter of the first and second cylinders 107a and 107b. Even with a configuration having a large outer diameter, a predetermined object can be achieved. In addition, since the first and second cylinders 107a and 107b and the guide 206 can be configured as integrally molded parts, productivity can be improved. Furthermore, since the outer diameter and thickness of the partition plate 505 can be reduced, it is possible to further improve productivity and reduce production costs.

Embodiment 6 FIG.
Hereinafter, the sixth embodiment of the present invention will be described based on the drawings, with a focus on differences from the first embodiment. FIG. 16 is a configuration diagram of the compression mechanism 600 of the two-cylinder rotary compressor according to the sixth embodiment of the present invention.
The first difference between the compression mechanism 600 and the compression mechanism 100 shown in FIG. 1 is that the first and second eccentric portions 602a and 602b provided integrally with the crankshaft 601 are not equipped with a rolling piston. This is a point having an outer diameter that is rotatable along the inner peripheral surfaces of the first and second cylinders 107a and 107b. The second difference is that the first compression chamber 608a faces the inner wall surface of the first cylinder head 109a, the outer peripheral surface of the first eccentric part 602a, and the first cylinder head 109a of the disk part 604. It is a point sealed by the board surface and the inner peripheral surface of the first cylinder 107a. The third difference is that the second compression chamber 608b faces the inner wall surface of the second cylinder head 109b, the outer peripheral surface of the second eccentric portion 602b, and the second cylinder head 109b of the disk portion 604. It is a point sealed by the board surface and the inner peripheral surface of the second cylinder 107b.

  Next, the internal mechanisms of the first and second compression chambers 608a and 608b in the compression mechanism unit 600 will be described focusing on differences from the compression mechanism unit 100 shown in the first embodiment. The compression mechanism unit 600 is different from the first embodiment in that the vane 110 provided in the first and second cylinders 107a and 107b has the first and second eccentric portions 602a and 602b by springs, gas pressure, and the like. By contacting the outer periphery, the low-pressure refrigerant and the high-pressure refrigerant in the first and second compression chambers 608a and 608b are blocked. Since the internal mechanisms other than those on the left are the same as those in the first embodiment, they are omitted.

  The refrigerant compression process will be described focusing on differences from the first embodiment. The difference from the compression mechanism 100 shown in the first embodiment is that, in the first and second compression chambers 608a and 608b, the outer peripheral surfaces of the first and second eccentric portions 602a and 602b are interposed via the rolling piston 103. Instead, the refrigerant flowing into the compression chambers is compressed by one rotation along the inner peripheral surfaces of the first and second compression chambers 608a and 608b. The other processes are the same as those in the first embodiment, and will be omitted.

  As described above, the first and second eccentric portions 602a and 602b provided integrally with the crankshaft 601 achieve the predetermined object even when the refrigerant and the refrigerant are directly compressed without using the rolling piston 103. Can do. Further, since it is not necessary to mount the rolling piston 103, the time required for the assembly process is shortened. As a result, productivity can be improved and costs can be reduced.

Embodiment 7 FIG.
In the following, the seventh embodiment of the present invention will be described based on the drawings, with a focus on differences from the fourth embodiment. FIG. 17 is a configuration diagram of a compression mechanism 700 of the two-cylinder rotary compressor according to the seventh embodiment of the present invention.
The first difference between the compression mechanism 700 and the compression mechanism 400 shown in FIG. 5 is that the first and second eccentric portions 702a and 602b provided integrally with the crankshaft 701 are not equipped with a rolling piston. This is a point having an outer diameter that is rotatable along the inner peripheral surfaces of the first and second cylinders 107a and 107b. The second difference is that the first compression chamber 708a includes the inner wall surface of the first cylinder head 109a, the outer peripheral surface of the first eccentric part 702a, the first cylinder head of the disk part 704 and the partition plate 705. It is a point sealed by the board surface which faces 109a, and the internal peripheral surface of the 1st cylinder 107a. The third difference is that the second compression chamber 708b includes the inner wall surface of the second cylinder head 109b, the outer peripheral surface of the second eccentric portion 602b, the second cylinder head of the disk portion 704 and the partition plate 705. It is a point sealed by the board surface facing 109b and the inner peripheral surface of the second cylinder 107b.

  The details of the first and second compression chambers 708a and 708b and the items of the compression process are the same as those in the sixth embodiment, and will be omitted.

  As described above, the first and second eccentric portions 702a and 602b provided integrally with the crankshaft 701 directly perform refrigerant compression without using the rolling piston 103. Can be achieved. Further, since it is not necessary to mount the rolling piston 103, the time required for the assembly process is shortened. As a result, productivity can be improved and costs can be reduced.

  It should be noted that the embodiment of the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.

100, 200, 300, 400, 500, 600, 700 compression mechanism,
101, 201, 301, 401, 601, 701 crankshaft,
102a, 402a, 602a, 702a first eccentric part,
102b, 602b second eccentric part, 103 rolling piston,
104, 204, 304, 404, 604, 704 disc part,
305,405,505,705 partition plate, 106,206 guide,
107a first cylinder, 107b second cylinder,
108a, 308a, 408a, 608a, 708a first compression chamber,
108b, 308b, 608b, 708b second compression chamber,
109a first cylinder head, 109b second cylinder head, 110 vane.

Claims (4)

In a two-cylinder rotary compressor having a crankshaft that is rotated by external power,
The compression mechanism is
A cylindrical first cylinder;
A cylindrical second cylinder arranged coaxially with the first cylindrical cylinder;
A first eccentric portion provided integrally with the crankshaft and rotating along an inner peripheral surface of the first cylinder;
A second eccentric portion provided integrally with the crankshaft and rotating along an inner peripheral surface of the second cylinder;
Between the first eccentric part and the second eccentric part, the first eccentric part, the second eccentric part, and the crankshaft are provided integrally and have the same rotation axis as the crankshaft. a disc portion for partitioning between the first eccentric part and said second eccentric portion,
An outer peripheral surface of the disk portion and an annular partition plate fitted to the first eccentric portion ;
A first cylinder head fixed to the first cylinder, sealing an opening surface of the first cylinder facing the partition plate, and supporting the crankshaft;
A second cylinder head that is fixed to the second cylinder, seals an opening surface of the second cylinder that faces the disk portion and the partition plate, and supports the crankshaft;
Sealed by an inner wall surface of the first cylinder head, an outer peripheral surface of the first eccentric portion, a panel surface of the partition plate facing the first cylinder head, and an inner peripheral surface of the first cylinder. A first compression chamber,
An inner wall surface of the second cylinder head, an outer peripheral surface of the second eccentric portion, a disk surface of the disk portion and the partition plate facing the second cylinder head, and an inner periphery of the second cylinder A second compression chamber sealed by a surface;
A two-cylinder rotary compressor characterized by forming The first eccentric portion and the second eccentric portion have a circular cross section perpendicular to the axial direction of the crankshaft, and are attached to the outer peripheral surfaces of the first eccentric portion and the second eccentric portion. The two-cylinder rotary compressor according to claim 1, further comprising a rolling piston. Between the first cylinder and the second cylinder, according to claim 1 or claim wherein the partition plate guide having an inner peripheral surface which is fitted sliding the outer circumferential surface of the is characterized in that it is sandwiched 2. A 2-cylinder rotary compressor according to 2. The two-cylinder rotary compressor according to any one of claims 1 to 3, wherein the partition plate is press-fitted, welded, or bonded to the disk portion.

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