WO2023181362A1 - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

Provided is a rotary compressor that can be made compact and that can prevent a drop in reliability of a multi-stage compression mechanism.　A compression mechanism (18) of a compressor (2) includes: a low pressure-side cylinder (55) having a low pressure-side compression chamber (61) that compresses an introduced gaseous refrigerant by the motive power of a low pressure-side eccentric part (51) and that discharges such refrigerant; a high pressure-side cylinder (57) that compresses the refrigerant discharged from the low pressure-side compression chamber (61) with the motive power of a high pressure-side eccentric part (52); and a partition plate (56) provided between the low pressure-side cylinder (55) and the high pressure-side cylinder (57). The height of the low pressure-side compression chamber (61) is the same as the height of the high pressure-side compression chamber (62), and the inner diameter dimension of the low pressure-side compression chamber (61) is greater than the inner diameter dimension of the high pressure-side compression chamber (62).

Description

Rotary compressor and refrigeration cycle equipment

Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle device.

A vertically placed cylindrical airtight container, a compression mechanism section disposed at a lower part of the airtight container, and a motor serving as an electric motor section arranged within the airtight container and above the compression mechanism section to drive the compression mechanism section; A rotary compressor is known that includes a rotating shaft. The rotation axis extends along a center line extending vertically of the closed container. The compression mechanism section is connected to the motor via a rotating shaft. The compression mechanism compresses refrigerant gas flowing from outside the closed container using the power of the rotating shaft.

The compression mechanism unit is connected to the first compression chamber, a first annular roller fitted in the first eccentric portion of the rotating shaft, a first blade that partitions an internal space of the first compression chamber, and the first compression chamber. It has a second compression chamber, a second annular roller fitted into a second eccentric portion of the rotating shaft, and a second blade that partitions an internal space of the second compression chamber. The first roller revolves along the inner wall surface of the first compression chamber, and the second roller revolves along the inner wall surface of the second compression chamber. The first compression chamber compresses refrigerant gas flowing in from the outside by the revolution of the first roller and discharges the compressed gas. This discharged refrigerant gas is further compressed in the second compression chamber by the revolution of the second roller.

International Publication No. 2021/033283

Here, the volume of the space in which the roller moves one rotation is called the excluded volume. In a conventional rotary compressor, the pressure of the refrigerant gas discharged from the first compression chamber is further increased in the second compression chamber, and a predetermined amount of refrigerant gas is made to have a high pressure, so the displaced volume of the first compression chamber is , is set larger than the predetermined displacement volume of the second compression chamber.

In order to increase the internal volume of the first cylinder relative to the displacement volume of the first compression chamber, for example, the height of the first compression chamber is set larger than the height of the second compression chamber. The height of the first blade arranged in the first compression chamber is greater than the height of the second blade arranged in the second compression chamber.

However, if the height of the first compression chamber is greater than the height of the second compression chamber, the height of the first blade will be greater than the height of the second blade. Generally, as the height of the blade increases, the load on the blade from, for example, refrigerant gas increases, which tends to reduce the reliability of blade operation. Moreover, if the height of the first compression chamber is made larger than the height of the second compression chamber, it will help to increase the size of the compression mechanism section and, in turn, increase the size of the compressor.

Therefore, an object of the present invention is to provide a rotary compressor that can prevent the reliability of a multistage compression mechanism from decreasing and can be downsized.

In order to solve the above problems, a rotary compressor according to an embodiment of the present invention includes a closed container having a central axis extending in the vertical direction, an electric motor section provided in the closed container, and a rotary compressor having a central axis extending in the vertical direction. a low-pressure side eccentric part that is eccentric from the central axis by a first eccentric length; and a high-pressure side eccentric part that is provided below the low-pressure side eccentric part and is eccentric from the central axis by a second eccentric length; a low-pressure side cylinder having a low-pressure side compression chamber that compresses and discharges an introduced gaseous refrigerant by the power of the low-pressure side eccentric part; a high-pressure side cylinder having a high-pressure side compression chamber that compresses the refrigerant discharged from the side compression chamber by the power of the high-pressure side eccentric part; a partition plate provided between the low-pressure side cylinder and the high-pressure side cylinder; a compression mechanism section having a compression mechanism, wherein the height of the low-pressure side compression chamber is the same as the height of the high-pressure side compression chamber, and the inner diameter dimension of the low-pressure side compression chamber is the inner diameter dimension of the high-pressure side compression chamber. bigger.

The first eccentric length of the rotary compressor according to the embodiment of the present invention is preferably larger than the second eccentric length.

The compression start angle of the high pressure side compression chamber of the rotary compressor according to the embodiment of the present invention is preferably larger than the compression start angle of the low pressure side compression chamber.

Preferably, the high-pressure side cylinder of the rotary compressor according to the embodiment of the present invention has a groove that is provided on a wall surface that partitions the high-pressure side compression chamber and connects to the suction portion of the high-pressure side compression chamber.

The partition plate and the high pressure side cylinder of the rotary compressor according to the embodiment of the present invention have an intermediate pressure passage, and the intermediate pressure passage includes a discharge part of the low pressure side compression chamber and a discharge part of the high pressure side compression chamber. It is preferable to connect it to the suction part.

The partition plate of the rotary compressor according to the embodiment of the present invention includes a first partition plate half and a second partition plate half stacked below the first partition plate half, A portion of the medium pressure flow path is provided on the mating surfaces of the first partition plate half and the second partition plate half, and the thickness of the second partition plate half below the portion of the medium pressure flow path is , is preferably larger than the thickness of the first partition plate half above a part of the medium pressure flow path.

The rotary compressor according to an embodiment of the present invention includes an intermediate pipe provided outside the closed container, and the intermediate pressure flow path may be connected to the suction part of the high pressure side compression chamber via the intermediate pipe. preferable.

Further, in order to solve the above-mentioned problems, a refrigeration cycle device according to an embodiment of the present invention includes the rotary compressor, the radiator, the expansion device, the heat absorber, the rotary compressor, the radiator, A refrigerant pipe is provided that connects the expansion device and the heat absorber and allows the refrigerant to flow therethrough.

According to the present invention, it is possible to provide a rotary compressor that can prevent the reliability of a multistage compression mechanism from decreasing and can be downsized.

1 is a schematic diagram of a refrigeration cycle device and a compressor according to an embodiment of the present invention. FIG. 2 is a plan cross-sectional view passing over the first cylinder of the compressor according to the embodiment of the present invention. FIG. 3 is a plan cross-sectional view passing over the second cylinder of the compressor according to the embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a partition plate of a compressor according to an embodiment of the present invention. FIG. 7 is a vertical cross-sectional view of another example of the partition plate of the compressor according to the embodiment of the present invention. (a) is a cross-sectional view taken along line B-B' shown in FIG. 3, and (b) is a partial cross-sectional view taken along line D-D' shown in (a). (a) is a cross-sectional view showing a modified example of the groove in the embodiment of the present invention, and (b) is a partial cross-sectional view taken along the line E-E' shown in (a). (a) is a sectional view showing a modified example of the groove in the embodiment of the present invention, and (b) is a partial sectional view taken along the line F-F' shown in (a). (a) is a sectional view showing a modified example of the groove in the embodiment of the present invention, and (b) is a partial sectional view taken along the line GG' shown in (a).

Embodiments of a compressor and a refrigeration cycle device according to the present invention will be described with reference to FIGS. 1 to 6. In addition, the same code|symbol is attached|subjected to the same or equivalent structure in several drawings.

FIG. 1 is a schematic diagram of a refrigeration cycle device and a compressor according to an embodiment of the present invention. In addition, in FIG. 1, the compressor is shown in a longitudinal section.

FIG. 2 is a plan cross-sectional view passing over the first cylinder of the compressor according to the embodiment of the present invention.

FIG. 3 is a plan cross-sectional view passing over the second cylinder of the compressor according to the embodiment of the present invention.

The refrigeration cycle device 1 according to this embodiment is, for example, an air conditioner. The refrigeration cycle device 1 includes a hermetic rotary compressor 2 (hereinafter simply referred to as "compressor 2") that compresses a gaseous refrigerant as a working fluid, such as carbon dioxide (CO2), and a compressor 2. A radiator 3 (condenser) that cools the high temperature and high pressure refrigerant discharged from the refrigerant, a first expansion device 4 (expansion valve) and a second expansion device 5 (expansion valve) that reduce the pressure of the cooled refrigerant, and a It includes a heat absorber 6 (evaporator) that evaporates the refrigerant, an accumulator 7 that separates the refrigerant into gas and liquid, a first refrigerant pipe 8, and a second refrigerant pipe 9.

The first refrigerant pipe 8 sequentially connects the compressor 2, the radiator 3, the first expansion device 4, the second expansion device 5, the heat absorber 6, and the accumulator 7 to flow the refrigerant. The accumulator 7 has an outlet pipe 12 that is connected to the compressor 2 and allows refrigerant to flow into the compressor 2. One end of the second refrigerant pipe 9 is connected to the first refrigerant pipe 8 between the first expansion device 4 and the second expansion device 5. The other end of the second refrigerant pipe 9 is connected to an intermediate pipe 13 of the compressor 2. The second refrigerant pipe 9 allows the refrigerant, which has been reduced in pressure to, for example, an intermediate pressure, in the first expansion device 4 to flow into the compressor 2 via the intermediate pipe 13 .

The compressor 2 includes a cylindrical airtight container 16 placed vertically, an electric motor section 17 housed in the upper half of the airtight container 16, and a compression mechanism section 18 housed in the lower half of the airtight container 16. , a crankshaft 19 that transmits the rotational driving force of the electric motor section 17 to the compression mechanism section 18 , a main bearing 21 that is provided below the electric motor section 17 and rotatably supports the crankshaft 19 , and A sub-bearing 22 that is provided below and cooperates with the main bearing 21 to rotatably support the crankshaft 19, a frame 23 that is fixed to the closed container 16 and supports the compression mechanism section 18, and an outer side of the closed container 16. An intermediate piping 13 provided in the intermediate piping 13 is provided.

The center line of the vertically placed closed container 16 extends in the vertical direction. The compressor 2 is installed with the center line of the closed container 16 facing vertically. The airtight container 16 includes a cylindrical body 26 extending in the vertical direction, an upper end plate 27 that closes the upper end of the body 26, and a lower end plate 28 that closes the lower end of the body 26. The closed container 16 stores lubricating oil for lubricating the compression mechanism section 18. Lubricating oil is supplied to the compression mechanism section 18 through an oil supply mechanism provided within the lower end of the crankshaft 19 .

The upper end plate 27 of the closed container 16 is equipped with a discharge pipe 31 that discharges the high temperature and high pressure refrigerant discharged into the closed container 16 from the compression mechanism section 18 to the outside of the closed container 16. The discharge pipe 31 is connected to the first refrigerant pipe 8. Further, the upper mirror plate 27 includes a terminal block 32 having a sealed terminal for guiding power from an external power source to the motor section 17. The sealed terminal of the terminal block 32 is provided across the outside and inside of the upper mirror plate 27.

The body 26 of the closed container 16 has a suction end 35 connected to the outlet pipe 12 of the accumulator 7, an intermediate discharge end 36 connected to one end of the intermediate piping 13, and an intermediate discharge end 36 connected to the other end of the intermediate piping 13. an intermediate suction end 37 connected to the end. The suction end 35 , the intermediate discharge end 36 , and the intermediate suction end 37 have a central portion fixed to the closed container 16 , an inner end located within the closed container 16 , and an inner end located outside the closed container 16 . and an outer end. Further, the body 26 of the airtight container 16 is provided with a fixture 38 such as a holder for fixing the accumulator 7 to the outer surface of the body 26 .

The intermediate pipe 13 allows the refrigerant compressed to an intermediate pressure by the compression mechanism section 18 to flow to the outside of the closed container 16. The intermediate pipe 13 is connected to a cylindrical external muffler 39 and an intercooler 41. The intermediate pipe 13 sequentially connects the intermediate discharge end 36, the external muffler 39, the intercooler 41, and the intermediate suction end 37 to allow the refrigerant to flow therethrough. The external muffler 39 has a cylindrical shape extending in the vertical direction, and is fixed to the outer surface of the closed container 16 by a fixture 38 such as a holder provided on the body 26 of the closed container 16. The intermediate pipe 13 allows the refrigerant compressed to an intermediate pressure by the compression mechanism section 18 to flow therethrough.

The electric motor section 17 generates a driving force that rotates the compression mechanism section 18. The electric motor section 17 includes a cylindrical stator 43 fixed to the inner surface of the airtight container 16, a rotor 44 disposed inside the stator 43 to generate rotational driving force for the compression mechanism section 18, and the stator 43. A plurality of lead wires 45 are drawn out from the terminal block 32 and electrically connected to the sealed terminals of the terminal block 32. The motor section 17 may be an open-winding type motor, a star-connected motor, or a motor having multiple systems, for example, two systems of three-phase windings.

The rotor 44 includes a rotor core (not shown) having a magnet housing hole, and a permanent magnet (not shown) accommodated in the magnet housing hole. The rotor 44 is fixed to the crankshaft 19. The rotation center line C of the rotor 44 and the crankshaft 19 substantially coincides with the center line of the stator 43. Further, the rotation center line C of the rotor 44 and the crankshaft 19 substantially coincides with the center line of the closed container 16.

The plurality of lead wires 45 are power lines that supply power to the stator 43, and are so-called lead wires. A plurality of lead wires 45 are wired depending on the type of motor section 17, that is, open winding type or star connection.

The crankshaft 19 connects the electric motor section 17 and the compression mechanism section 18. The crankshaft 19 rotates integrally with the rotor 44 and extends downward from the rotor 44. The crankshaft 19 includes a main shaft portion 47 located in an intermediate portion, a plurality of eccentric portions 48 located below the main shaft portion 47, and a counter shaft portion 49 located below the plurality of eccentric portions 48. There is. The main shaft portion 47 is rotatably supported by the main bearing 21 , and the counter shaft portion 49 is rotatably supported by the counter bearing 22 . The main bearing 21 and the sub-bearing 22 are also part of the compression mechanism section 18. In other words, the crankshaft 19 is disposed to penetrate the compression mechanism section 18. Each eccentric portion 48 is a so-called crank pin. The plurality of eccentric parts 48 include, for example, a first eccentric part 51 and a second eccentric part 52. The first eccentric portion 51 and the second eccentric portion 52 have a disk shape or a cylindrical shape with centers that do not match the rotation center line C of the crankshaft 19.

The compression mechanism section 18 sucks and compresses gaseous refrigerant from the outlet pipe 12 and the intermediate pipe 13 by rotation of the crankshaft 19, and discharges the refrigerant compressed to high temperature and high pressure into the closed container 16. The compression mechanism section 18 is a multistage rotary compression mechanism. The compression mechanism section 18 includes a first cylinder 55 disposed below the main bearing 21 , a partition plate 56 disposed below the first cylinder 55 , and a second cylinder disposed between the partition plate 56 and the sub-bearing 22 . It is equipped with two cylinders 57.

The main bearing 21, the first cylinder 55, the partition plate 56, the second cylinder 57, and the sub-bearing 22 are arranged to overlap in the vertical direction. The main bearing 21 covers the upper surface of the first cylinder 55. The secondary bearing 22 covers the lower surface of the second cylinder 57. The partition plate 56 closes off the lower surface of the first cylinder 55 and the upper surface of the second cylinder 57.

The first cylinder 55 is fixed by fastening members 59 such as bolts to the frame 23 which is fixed to the body 26 of the closed container 16 at a plurality of locations by welding. The main bearing 21, the first cylinder 55, the partition plate 56, the second cylinder 57, and the sub-bearing 22 are fixed to each other by a plurality of fastening members 59 such as bolts. The main bearing 21 , the first cylinder 55 , the partition plate 56 , the second cylinder 57 , and the sub-bearing 22 are fixed within the closed container 16 via the frame 23 .

The first cylinder 55 has a first compression chamber 61 that passes through the first cylinder 55 in the vertical direction. The second cylinder 57 has a second compression chamber 62 that passes through the second cylinder 57 in the vertical direction. The first compression chamber 61 and the second compression chamber 62 are disk-shaped spaces, and overlap in the vertical direction with the partition plate 56 in between. The center of the first compression chamber 61 and the center of the second compression chamber 62 are arranged on the rotation center line C. The compression mechanism section 18 compresses the low-pressure gas refrigerant flowing from the accumulator 7 to an intermediate pressure in the first compression chamber 61 and discharges the compressed gas refrigerant. Further, the compression mechanism section 18 compresses the intermediate pressure gas refrigerant discharged from the first compression chamber 61 to a high pressure in the second compression chamber 62 and discharges the compressed gas refrigerant. The first cylinder 55 and the second cylinder 57 may be collectively referred to as " cylinders 55, 57," and the first compression chamber 61 and second compression chamber 62 may be collectively referred to as " compression chambers 61, 62." There is.

Further, the compression mechanism section 18 includes a first annular roller 63 disposed in the first compression chamber 61, a second annular roller 64 disposed in the second compression chamber 62, and a second annular roller 64 in the first cylinder 55. The first blade 65 is arranged in the radial direction of the first compression chamber 61, and the second blade 66 is arranged in the radial direction of the second compression chamber 62 in the second cylinder 57. The first roller 63 and the second roller 64 may be collectively referred to as " rollers 63, 64," and the first blade 65 and second blade 66 may be collectively referred to as " blades 65, 66." The rollers 63, 64 are so-called rolling pistons, and the blades 65, 66 are so-called vanes.

The first roller 63 is fitted into the first eccentric portion 51 of the crankshaft 19. The second roller 64 fits into the second eccentric portion 52 of the crankshaft 19 . The crankshaft 19 rotates counterclockwise when the compressor 2 is viewed from above. When the crankshaft 19 is rotating, the two eccentric parts 48, that is, the first eccentric part 51, the second eccentric part 52, the first roller 63, and the second roller 64, seen from above of the crankshaft 19 are , rotates counterclockwise around the rotation center line C (see FIG. 1) as indicated by the solid arrow R1 shown in FIG. The rotation direction of the crankshaft 19 and the rollers 63 and 64 may be referred to as a "rotation direction R1," and the counter-rotation direction of the rotation direction R1 may be referred to as a "counter-rotation direction R2."

The rollers 63 and 64 rotate eccentrically with respect to the center axes of the cylinders 55 and 57 and the rotation center line C of the crankshaft 19 while contacting the inner walls of the cylinders 55 and 57 as the crankshaft 19 rotates.

The blades 65 and 66 are arranged in a straight line in the vertical direction. In other words, the two blades 65 and 66 are arranged at substantially the same position in the circumferential direction of the cylinders 55 and 57. Further, the blades 65 and 66 are pressed against the rollers 63 and 64 by blade springs (not shown). Therefore, the blades 65 and 66 reciprocate in the radial direction of the compression chambers 61 and 62 while being pushed by the rollers 63 and 64 due to the rotation of the crankshaft 19. As shown in FIGS. 2 and 3, the blades 65, 66 divide the space between the cylinders 55, 57 and the rollers 63, 64 into a suction space S1 (not shown in FIG. 2) and a compression space S2. The height of the first blade 65 is the same as the height of the second blade 66. The height of the blades 65, 66 is approximately the same as the height of the compression chambers 61, 62.

The first cylinder 55 has a first suction section 68 and a first discharge section 69 that are connected to the first compression chamber 61. The first suction portion 68 extends outward from the inner wall surface of the first compression chamber 61 , and has an outer end connected to an inner end of the suction end portion 35 of the closed container 16 . The first discharge portion 69 is, for example, recessed outward from the inner wall surface of the first compression chamber 61 and opens to the lower surface of the first cylinder 55. The first suction part 68 is arranged adjacent to the first blade 65 in the rotational direction R1, and the first discharge part 69 is arranged adjacent to the first blade 65 in the opposite rotational direction R2.

The second cylinder 57 has a second suction section 71 and a second discharge section 72 that are connected to the second compression chamber 62. The second suction portion 71 extends outward from the inner wall surface of the second compression chamber 62 and has an outer end connected to an inner end of the intermediate suction end portion 37 of the closed container 16 . The second discharge portion 72 is, for example, recessed outward from the inner wall surface of the second compression chamber 62 and opens at the lower surface of the second cylinder 57 . The second suction section 71 is arranged side by side on the rotational direction R1 side of the second blade 66, and the second discharge section 72 is arranged adjacent to the second blade 66 on the opposite rotational direction R2 side. The first suction part 68 and the second suction part 71 may be collectively referred to as " suction parts 68, 71", and the first discharge part 69 and second discharge part 72 may be collectively referred to as "discharge parts 69, 72". It is sometimes called.

The partition plate 56 and the second cylinder 57 have an intermediate pressure passage 75 connected to the first discharge part 69 of the first compression chamber 61. The intermediate pressure flow path 75 is a flow path for the refrigerant that has been compressed in the first compression chamber 61 and has an intermediate pressure. The medium pressure passage 75 of the partition plate 56 includes a passage provided within the partition plate 56 and extending along the upper and lower surfaces of the partition plate 56. The intermediate pressure passage 75 of the second cylinder 57 includes a crank-shaped passage provided outside the second compression chamber 62 and bent outward from the upper side. The intermediate pressure passage 75 of the partition plate 56 is connected to the first discharge part 69 of the first compression chamber 61, and the intermediate pressure passage 75 of the second cylinder 57 is connected to the inner end of the intermediate discharge end 36 of the closed container 16. has been done.

The partition plate 56 is equipped with a first discharge valve 76 that discharges the refrigerant compressed within the first compression chamber 61 to the intermediate pressure flow path 75. The first discharge valve 76 opens a discharge port (not shown) when the pressure difference between the pressure in the first compression chamber 61 and the pressure in the intermediate pressure channel 75 reaches a predetermined value due to the compression operation of the compression mechanism section 18. Then, the refrigerant compressed to medium pressure is discharged to the medium pressure flow path 75 of the partition plate 56. The refrigerant discharged into the intermediate pressure passage 75 of the partition plate 56 is guided out of the closed container 16 from the intermediate discharge end 36 via the intermediate pressure passage 75 of the second cylinder 57 . The refrigerant led out of the closed container 16 flows through the intermediate pipe 13, is led into the inside of the closed container 16 from the intermediate suction end 37, and is transferred from the second suction section 71 of the second cylinder 57 to the second compression chamber. 62.

The main bearing 21, the first cylinder 55, the partition plate 56, the second cylinder 57, and the sub-bearing 22 have a high-pressure passage 79 that passes through them in the vertical direction and is connected to each other. The high-pressure flow path 79 is a high-pressure gas refrigerant flow path that extends linearly in the vertical direction across the main bearing 21, the first cylinder 55, the partition plate 56, the second cylinder 57, and the sub-bearing 22.

The compression mechanism section 18 includes a second discharge valve 81 that is provided in the sub-bearing 22 and discharges the refrigerant compressed in the second compression chamber 62, and a first discharge valve that covers the second discharge valve 81 and the high-pressure flow path 79. It is equipped with a muffler 82. The second discharge valve 81 is connected to a discharge port (not shown) when the pressure difference between the pressure in the second compression chamber 62 and the pressure in the first discharge muffler 82 reaches a predetermined value due to the compression action of the compression mechanism section 18. ) is opened to discharge the highly compressed refrigerant into the first discharge muffler 82. The refrigerant discharged from the second discharge valve 81 into the first discharge muffler 82 is guided above the compression mechanism section 18 through the high-pressure flow path 79. Note that the first discharge valve 76 and the second discharge valve 81 may be collectively referred to as "discharge valves 76, 81."

Furthermore, the compression mechanism section 18 includes a second discharge muffler 83 that is provided on the main bearing 21 and covers the high pressure flow path 79. The second discharge muffler 83 partitions a space into which high-pressure refrigerant is discharged from the high-pressure flow path 79. The second discharge muffler 83 has a discharge hole (not shown) that connects the inside and outside of the second discharge muffler 83 . The high-pressure refrigerant discharged into the second discharge muffler 83 is discharged into the closed container 16 through the discharge hole.

FIG. 4 is a longitudinal sectional view of a partition plate of a compressor according to an embodiment of the present invention.

As shown in FIGS. 1 and 4, the partition plate 56 is a laminate of a plurality of plates that are stacked one above the other. The partition plate 56 includes a first partition plate half 91 and a second partition plate half 92 that overlap in the vertical direction. The substantial shape of the first partition plate half 91 and the second partition plate half 92 is a disk shape with substantially the same thickness. The first partition plate half 91 disposed on the upper side has a recess 91a (dent, groove) open to the lower surface of the first partition plate half 91. The second partition plate half 92 arranged on the lower side has a recess 92a (dent, groove) open to the upper surface of the second partition plate half 92. The medium pressure flow path 75 of the partition plate 56 is a space defined by a recess 91a (dent, recess) of the first partition plate half 91 and a recess 92a (dent, recess) of the second partition plate half 92. . The first partition plate half 91 has a hole 91b that connects the recess 91a to the first compression chamber 61. The first discharge valve 76 is provided in the recess 91a of the first partition plate half 91 to open and close the hole 91b. The second partition plate half 92 has a hole 92b that connects the recess 92a to the medium pressure passage 75 of the second cylinder 57.

The vertical thickness of the first partition plate half 91 and the vertical thickness of the second partition plate half 92 are substantially the same, while the depth of the recess 92a of the second partition plate half 92 is substantially the same. The depth is shallower than the depth of the recess 91a of the first partition plate half 91. In other words, the thickness t2 of the bottom plate portion of the recess 92a of the second partition plate half 92 is thicker than the thickness t1 of the bottom plate portion of the recess 91a of the first partition plate half 91. The bottom plate portion of the recess 91 a of the first partition plate half 91 closes the first compression chamber 61 , and the bottom plate portion of the recess 92 a of the second partition plate half 92 closes the second compression chamber 62 .

Incidentally, the multi-stage compression mechanism section 18 compresses low-pressure refrigerant into medium-pressure refrigerant in the first compression chamber 61, and compresses medium-pressure refrigerant into high-pressure refrigerant in the second compression chamber 62. That is, the second partition plate half 92 bears a higher pressure load than the first partition plate half 91. Therefore, by making the thickness t2 of the bottom plate portion of the recess 92a of the second partition plate half 92 thicker than the thickness t1 of the bottom plate portion of the recess 91a of the first partition plate half 91, the The rigidity of the first partition plate half 91 and the second partition plate half 92 overlapping the second cylinder 57 are optimized. In other words, the rigidity of the partition plate 56, which is a laminate of the first partition plate half 91 and the second partition plate half 92, is optimized. The partition plate 56 whose rigidity is optimized appropriately prevents refrigerant leakage at both the mating surfaces of the first compression chamber 61 and the partition plate 56 and the mating surfaces of the second compression chamber 62 and the partition plate 56.

Here, the suction pressure Ps of the first compression chamber 61, the intermediate pressure Pm discharged from the first compression chamber 61 and supplied to the second compression chamber 62 via the intermediate pressure flow path 75, and the discharge pressure of the second compression chamber 62. Pd has a relationship of (suction pressure Ps)<(intermediate pressure Pm)<(discharge pressure Pd). During operation, the condition (Pd-Pm)>(Pm-Ps) always holds true. Under these conditions, each pressure will vary depending on the operating conditions. The intermediate pressure Pm changes according to the relationship Pm=√(Pd×Ps).

Therefore, the surface pressure load of the differential pressure (Pm-Ps) acts on the recess 91a of the first partition plate half 91, and the surface pressure load of the differential pressure (Pd-Pm) acts on the recess 92 of the second partition plate half 92. 92a.

The first partition plate half 91 and the second partition plate half 92 have substantially the same thickness dimension, while the thickness t2 of the bottom plate portion of the second partition plate half 92 is different from that of the first partition plate half. It is thicker than the thickness t1 of the bottom plate portion of the half body 91. These dimensional relationships optimize the required stiffness of the partition plate 56.

By making the thickness dimensions of the first partition plate half 91 and the second partition plate half 92 the same, the material of the first partition plate half 91 and the second partition plate half 92 can be made common. . In addition, by providing recesses in both the first partition plate half 91 and the second partition plate half 92 that face each other vertically, the passage area of the intermediate pressure flow path 75 is maintained, and the entire partition plate 56 is The rigidity can be improved. When the rigidity of the partition plate 56 as a whole is improved, deformation of the partition plate 56 is suppressed, and refrigerant leakage from the intermediate pressure channel 75 is prevented.

Further, the thickness t3 near the valve seat where the hole 91b and the first discharge valve 76 are arranged may be equal to or smaller than t1. Thereby, the volume of the hole 91b portion can be reduced while ensuring the necessary rigidity against the pressure difference.

The refrigerant in the volume of the hole 91b is not discharged from the first cylinder 55. Therefore, the holes 91b become dead volumes, resulting in a decrease in volumetric efficiency and a decrease in the efficiency of the compressor. Therefore, by setting the range of t3≦t1<t2, the dead volume of the hole 91b is reduced, and a decrease in efficiency of the compressor 2 is suppressed.

Further, by arranging the intermediate pressure passage 75 formed by the recesses 91a and 92a on the mating surfaces of the partition plate 56, the degree of freedom in arranging the passages inside and outside the compressor 2 is improved.

Note that if the thickness of the first partition plate half 91 and the second partition plate half 92 are the same, the mating surfaces of the first partition plate half 91 and the second partition plate half 92 will be the same as that of the partition plate half 91. 56 in the substantial center in the vertical direction. The mating surfaces of the first partition plate half 91 and the second partition plate half 92 are arranged below the substantial center in the vertical direction of the partition plate 56, as indicated by the two-dot chain line MP1 in FIGS. It's okay. For example, the vertical thickness of the second partition plate half 92 is made thinner and uniform to eliminate the recess 92a, while the vertical thickness of the first partition plate half 91 is increased. A deeper recess 91a may be provided only in the first partition plate half 91. The depth of the recess 91a in this case should be equal to the recesses 91a and 92a in the case where the recesses 91a and 92a are provided in both the first partition plate half 91 and the second partition plate half 92, respectively.

Further, the mating surfaces of the first partition plate half 91 and the second partition plate half 92 are moved upward from the substantial center in the vertical direction of the partition plate 56, as indicated by the two-dot chain line MP2 in FIGS. With this arrangement, the rigidity of the second partition plate half 92 is further improved. For example, the vertical thickness of the first partition plate half 91 is made thinner and uniform to eliminate the recess 91a, while the vertical thickness of the second partition plate half 92 is increased. A deeper recess 92a may be provided only in the second partition plate half 92. The depth of the recess 92a in this case should be equal to the recesses 91a and 92a in the case where the recesses 91a and 92a are provided in both the first partition plate half 91 and the second partition plate half 92, respectively. By doing so, the rigidity of the second partition plate half 92 that closes the second compression chamber 62 is further improved.

That is, the partition plate 56 has a recess that defines the medium pressure flow path 75 in at least one of the first partition plate half 91 and the second partition plate half 92, that is, at least one of the recesses 91a and 92a. It's fine as long as it's there.

FIG. 5 is a longitudinal sectional view of another example of the partition plate of the compressor according to the embodiment of the present invention.

As shown in FIG. 5, the partition plate 56A includes a second partition plate half 92 that is thicker than the first partition plate half 91, and a second partition plate half 92 that is deeper than the recess 91a of the first partition plate half 91. The partition plate half body 92 may have a recessed portion 92a. The partition plate 56A configured in this manner can have sufficient rigidity even when the pressure on the higher stage side becomes higher.

Note that the compression mechanism including the first cylinder 55, the first eccentric portion 51, the first roller 63, and the first blade 65 disposed above and its components are referred to as "low pressure side" instead of "first". The compression mechanism and its components, including the second cylinder 57, second eccentric part 52, second roller 64, and second blade 66 arranged below, may be referred to as "second". It is sometimes called with the ``high pressure side'' added. For example, the first cylinder 55 is called the low pressure side cylinder 55, and the second cylinder 57 is called the high pressure side cylinder 57. The compression mechanism arranged above may be called a low-stage compression mechanism, and the compression mechanism arranged below may be called a high-stage compression mechanism.

Further, the intermediate pipe 13 includes an upstream intermediate pipe 13u that connects the first compression chamber 61 to the external muffler 39, a midway pipe 13m that connects the external muffler 39 to the intercooler 41, and a downstream side that connects the intercooler 41 to the second compression chamber 62. It includes an intermediate pipe 13d.
The upstream intermediate pipe 13u guides the medium-pressure refrigerant gas discharged from the first compression chamber 61 to the outside of the closed container 16.

The downstream intermediate pipe 13d joins the second refrigerant pipe 9 outside the closed container 16. Note that the pipe on the downstream side from the junction of the downstream intermediate pipe 13d and the second refrigerant pipe 9 serves both as the second refrigerant pipe 9 and the downstream intermediate pipe 13d. The downstream intermediate pipe 13d guides the medium-pressure refrigerant gas discharged from the external muffler 39 and passed through the intercooler 41 to the second compression chamber 62 inside the closed container 16.

In addition to the external muffler 39 provided on the discharge side of the first compression chamber 61, the compressor 2 may include a second external muffler 101 provided on the suction side of the second compression chamber 62. The external muffler 39 reduces pressure pulsations of the medium-pressure refrigerant gas discharged from the first compression chamber 61. Reducing the pressure pulsation reduces vibrations in the intermediate pipe 13 that are excited by the refrigerant gas flowing downstream from the external muffler 39. The second external muffler 101 is connected to a pipe that serves both as the second refrigerant pipe 9 and the downstream intermediate pipe 13d. The second external muffler 101 reduces pressure pulsations of the medium-pressure refrigerant gas sucked into the second compression chamber 62. Reducing pressure pulsations reduces vibrations of the intermediate pipe 13, vibrations of the compressor 2, and ambient noise, thereby ensuring reliability.

Hereinafter, the cylinders 55 and 57, the rollers 63 and 64, and the eccentric portion 48 of the crankshaft 19 will be further explained.

The height of the first cylinder 55 is approximately the same as the height of the first compression chamber 61. The height of the second cylinder 57 is approximately the same as the height of the second compression chamber 62. The height of the first compression chamber 61 and the height of the second compression chamber 62 are the same. The inner diameter dimension D1 of the first compression chamber 61 is larger than the inner diameter dimension D2 of the second compression chamber 62. The volume of the first compression chamber 61 is larger than the volume of the second compression chamber 62.

The inner wall surface of the first compression chamber 61 having the inner diameter dimension D1 and the inner wall surface of the second compression chamber 62 having the inner diameter dimension D2 are provided inside the inner wall surface of the intermediate pressure flow path 75 provided in the partition plate 56 in plan view. . The inner wall surface of the intermediate pressure channel 75 provided in the partition plate 56 includes, for example, a surface parallel to the rotation center line C.

As shown in FIG. 2, the first eccentric portion 51 of the crankshaft 19 is eccentric from the rotation center line C by a first eccentric length L1. In other words, the first eccentric length L1 of the first eccentric portion 51 is the length from the rotation center line C to the center of the first eccentric portion 51. As shown in FIG. 3, the second eccentric portion 52 of the crankshaft 19 is eccentric from the rotation center line C by a second eccentric length L2. In other words, the second eccentric length L2 of the second eccentric portion 52 is the length from the rotation center line C to the center of the second eccentric portion 52. The second eccentric length L2 is preferably smaller than the first eccentric length L1. Note that the first eccentric part 51 and the second eccentric part 52 are eccentric with a phase difference of 180 degrees, and FIGS. 2 and 3 show the states of the eccentric parts at the same timing.

The center of the first roller 63 coincides with the center of the first eccentric portion 51. The first roller 63 rotates eccentrically from the rotation center line C by a first eccentric length L1. The center of the second roller 64 coincides with the center of the second eccentric portion 52. The second roller 64 rotates eccentrically from the rotation center line C by a second eccentric length L2.

The suction space S1 of the compression chambers 61, 62 defined by the blades 65, 66 and the rollers 63, 64 is connected to the rollers 63, 64 and the inner wall surface of the compression chambers 61, 62 from the surface on the rotation direction R1 side of the blades 65, 66. This is the space up to the contact point. The compression space S2 is a space from the surfaces of the blades 65 and 66 on the opposite rotational direction R2 to the contact points between the rollers 63 and 64 and the inner wall surfaces of the compression chambers 61 and 62. In other words, among the spaces separated by the blades 65, 66 and rollers 63, 64 in the cylinders 55, 57, the space connected to the suction parts 68, 71 is the suction space S1, and the space connected to the discharge parts 69, 72 is the suction space S1. is the compressed space S2. For example, when the rollers 63 and 64 are located in the direction of the blades 65 and 66, the spaces connected to the suction sections 68 and 71 and the discharge sections 69 and 72 are not distinguished as a suction space S1 and a discharge space S2.

(a) of FIG. 6 is a cross-sectional view taken along the line B-B' shown in FIG. 3, and (b) is a partial cross-sectional view taken along the line D-D' shown in (a). In FIG. 6A, the second eccentric portion 52, the second roller 64, and the second blade 66 are omitted.

As shown in FIGS. 3 and 6, the second cylinder 57 has a groove 104 between the second blade 66 and the second suction part 71. The groove 104 is arranged adjacent to the second blade 66 on the rotation direction R1 side. The groove 104 extends along the inner wall surface of the second compression chamber 62 from the rotational direction R1 side of the second blade 66 to the opposite rotational direction R2 side of the second suction section 71. The edge of the groove 104 on the rotational direction side is connected to the second suction portion 71 . The groove 104 is provided by recessing the upper part of the inner wall surface of the second compression chamber 62 toward the outside.

Hereinafter, the refrigerant suction operation and compression operation of the compression chambers 61 and 62 will be explained.

The rollers 63 and 64 of the compression mechanism section 18 are rotated within the compression chambers 61 and 62 of the cylinders 55 and 57 by the rotational power of the electric motor section 17. The suction spaces S1 of the compression chambers 61 and 62 are expanded when the rollers 63 and 64 located in the direction of the blades 65 and 66 begin to rotate in the rotational direction R1, and refrigerant flows in from the suction portions 68 and 71. The compression space S2 is reduced when the rollers 63 and 64 located in the direction of the blades 65 and 66 begin to rotate in the rotation direction R1, and the refrigerant in the compression space S2 is compressed and discharged from the discharge portions 69 and 72.

The suction start angle α at which suction of refrigerant starts in the suction space S1 is the angle at which the rollers 63 and 64 located in the direction of the blades 65 and 66 rotate in the rotation direction R1 and the refrigerant begins to flow from the suction portions 68 and 71. is the displacement angle. The suction start angle α1 of the first compression chamber 61 is the angle between the center line of the first blade 65 and the center line of the first suction portion 68 when the first compression chamber 61 is viewed from above. The suction start angle α2 of the second compression chamber 62 is a line connecting the center line of the second blade 66, the tip of the groove 104 on the second blade 66 side, and the rotation center line C when the second compression chamber 62 is viewed from above. is the angle between The suction start angle α1 of the first compression chamber 61 and the suction start angle α2 of the second compression chamber 62 are substantially the same.

Until the rollers 63 and 64 rotate from the direction of the suction parts 68 and 71 toward the direction of rotation R1 and the direction of the discharge parts 69 and 72, the refrigerant flows into the suction space S1 communicating with the suction parts 68 and 71.

That is, in the first cylinder 55, while the roller 63 rotates from the direction of the blade 65 to the suction start angle α1=β1, there is no distinction between the suction space S1 and the discharge space S2. The refrigerant flows into the suction space S1 communicating with the suction part 68 until the roller 63 rotates in the rotation direction R1 from the position of the angle α1 (=β1), which is the direction of the suction part 68, and reaches the discharge part 69.

Furthermore, in the second cylinder 57, while the roller 64 rotates from the direction of the blade 66 to the compression start angle β2, there is no distinction between the suction space S1 and the discharge space S2. The refrigerant flows into the suction space S1 communicating with the suction part 71 until the roller 63 rotates in the rotation direction R1 from the position of the angle β2, which is the orientation of the suction part 68, and reaches the discharge part 69.

The compression start angle β at which compression of the refrigerant starts in the compression space S2 is determined by the positions of the rollers 63 and 64 in the direction of the blades 65 and 66, and the position of the rollers 63 and 64 that rotate in the rotation direction R1 and start compression of the refrigerant. is the central angle with. The compression start angle β1 of the first compression chamber 61 is the angle between the center line of the first blade 65 and the center line of the first suction portion 68 when the first compression chamber 61 is viewed from above. The compression start angle β2 of the second compression chamber 62 is the angle between the center line of the second blade 66 and the center line of the second suction portion 71 when the second compression chamber 62 is viewed from above. The compression start angle β2 of the second compression chamber 62 is larger than the compression start angle β1 of the first compression chamber 61.

While the rollers 63, 64 rotate from the orientation of the blades 65, 66 to the compression start angle β, that is, while the rollers 63, 64 rotate by β degrees from the orientation of the blades 65, 66, the compression space S2 is (The compression space S2 of the second compression chamber 62 is connected to the second suction portion 71 and the groove 104). Therefore, the refrigerant flows out to the suction parts 68 and 71 (the second suction part 71 and the groove 104 in the compression space S2 of the second compression chamber 62), and the refrigerant is generally not compressed. Until the rollers 63, 64 rotate from the direction of the suction parts 68, 71 to the direction of the blades 65, 66, that is, while the rollers 63, 64 rotate (360-β) degrees from the suction parts 68, 71, compression The space S2 is not connected to the suction parts 68 and 71 (the second suction part 71 and the groove 104 in the compression space S2 of the second compression chamber 62). Therefore, the refrigerant is compressed. At this time, when the pressure in the compression space S2 rises to a predetermined pressure, the discharge holes of the discharge valves 76 and 81 are opened, and refrigerant at a predetermined pressure is discharged from the discharge portions 69 and 72.

When the rollers 63 and 64 rotate (360-β) degrees in this way and are positioned in the direction of the blades 65 and 66, the volume of the compression space S2 becomes zero, and all the refrigerant in the compression space S2 is discharged. Complete. When the rollers 63, 64 in the direction of the blades 65, 66 make one revolution, the displacement volume of the refrigerant discharged from the discharge portions 69, 72 of the compression space S2 is the volume of the compression chambers 61, 62, the volume of the rollers 63, 64, It is set by the outer diameter dimensions d1 and d2, the heights of the cylinders 55 and 57, and the compression start angle β. Therefore, the displacement volume of the first compression chamber 61 is set larger than the displacement volume of the second compression chamber 62, and the compression efficiency of the compressor 2 is effectively improved.

As shown in FIGS. 6(a) and 6(b), the groove 104 is provided by recessing only the upper part of the inner wall surface of the second compression chamber 62 toward the outside. It is not limited to this as long as it is connected to.

FIG. 7(a) is a sectional view showing a modified example of the groove in the embodiment of the present invention, and FIG. 7(b) is a partial sectional view taken along the line E-E' shown in FIG. 7(a).

FIG. 8(a) is a sectional view showing a modification of the groove in the embodiment of the present invention, and FIG. 8(b) is a partial sectional view taken along the line F-F' shown in FIG. 8(a).

FIG. 9(a) is a sectional view showing a modification of the groove in the embodiment of the present invention, and FIG. 9(b) is a partial sectional view taken along the line GG' shown in FIG. 9(a). 7(a), FIG. 8(a), and FIG. 9(a) are cross-sectional views of the same parts as FIG. 6(a), and show the second eccentric part 52, the second roller 64, and the second blade 66. It is omitted.

As shown in FIGS. 7(a) and 7(b), a groove 104e, which is a modification of the groove 104, concave at least one of the upper and lower parts of the inner wall surface of the second compression chamber 62 outward. It may also be provided. As shown in FIGS. 8(a) and 8(b), a groove 104f, which is a modified example of the groove 104, extends only the intermediate portion between the upper and lower parts of the inner wall surface of the second compression chamber 62 toward the outside. It may be provided in a recessed manner. Further, the cross-sectional shape of these grooves 104, 104e, and 104f is a stepped shape in which the inner wall surface of the second compression chamber 62 is recessed outward, but is not limited to this. For example, as shown in FIG. 9(b), a groove 104g, which is a modification of the groove 104, may have a tapered cross-sectional shape.

Further, although the groove 104 extends along the inner wall surface of the second compression chamber 62 from the rotation direction R1 side of the second blade 66 to the second suction portion 71, the groove 104 is not limited thereto. It is sufficient that the groove 104 is connected to the second suction portion 71 and that the compression start angle β2 can be set larger than the compression start angle β1 of the first compression chamber 61. For example, the groove 104 may extend along at least one of the rotation direction R1 side and the counter-rotation direction R2 side of the second suction portion 71. In this case, it is preferable that the suction start angle α2 be substantially the same as the suction start angle α1 of the first compression chamber 61. In order to do so, for example, the second suction part 71 is arranged adjacent to the rotational direction side of the second blade 66, the groove 104 is arranged adjacent to the rotational direction side of the second suction part 71, and It is sufficient that it extends along the rotation direction R1.

As described above, the refrigeration cycle device 1 and the compressor 2 according to the present embodiment have a compression mechanism that includes the low-pressure side cylinder 55 including the low-pressure side compression chamber 61 and the high-pressure side cylinder 57 including the high-pressure side compression chamber 62. 18. The height of the low pressure side compression chamber 61 is the same as the height of the high pressure side compression chamber 62, and the inner diameter dimension D1 of the low pressure side compression chamber 61 is larger than the inner diameter dimension D2 of the high pressure side compression chamber 62. Therefore, the volume of the high-pressure side compression chamber 62 is smaller than the volume of the low-pressure side compression chamber 61, and the displaced volume of the high-pressure side compression chamber 62 is smaller than the displaced volume of the low-pressure side compression chamber 61. Thereby, the compression efficiency of the multi-stage compression compressor 2 is improved. Further, the heights of the cylinders 55 and 57 are the same, and the difference in volume between the cylinders 55 and 57 is not set by the difference in height, but by the difference in inner diameter dimensions of the compression chambers 61 and 62. . Therefore, the height dimensions of the blades 65 and 66 are substantially unified. The operation of blades 65 and 66 whose heights are unified is easy to stabilize. Furthermore, the compression mechanism section 18 is reduced in size mainly in the height direction.

Furthermore, the refrigeration cycle device 1 and the compressor 2 according to the present embodiment have a low-pressure side eccentric portion 51 that is eccentric from the central axis of the closed container 16 by a first eccentric length L1, and a second eccentric portion 51 that is eccentric from the central axis of the closed container 16. The crankshaft 19 includes a high-pressure side eccentric portion 52 that is eccentric with a length L2. The first eccentric length L1 of the low pressure side eccentric part 51 is larger than the second eccentric length L2 of the high pressure side eccentric part 52. Therefore, the outer diameter of the low-pressure side roller 63 that fits into the low-pressure side eccentric portion 51 becomes small, and the displacement volume of the low-pressure side compression chamber 61 becomes large. Further, the outer diameter of the high-pressure side roller 64 that fits into the high-pressure side eccentric portion 52 becomes large, and the displacement volume of the high-pressure side compression chamber 62 becomes small. Therefore, the compression efficiency of the compressor 2 is further improved, and expansion of the compression mechanism section 18 is suppressed.

Further, in the refrigeration cycle device 1 and compressor 2 according to the present embodiment, the compression start angle β1 of the high pressure side compression chamber 62 is set to be larger than the compression start angle β2 of the low pressure side compression chamber 61. Therefore, the displacement volume of the high pressure side compression chamber 62 becomes small. Therefore, the compression efficiency of the compressor 2 is further improved, and expansion of the compression mechanism section 18 is suppressed.

Furthermore, the refrigeration cycle device 1 and the compressor 2 according to the present embodiment include a high-pressure side cylinder having a groove 104 provided in a wall surface that partitions a high-pressure side compression chamber 62 and connected to a high-pressure side suction part 71 of the high-pressure side compression chamber 62. It is equipped with 57. Therefore, the suction start angle α2 of the suction space S1 of the high-pressure side compression chamber 62 can be set small, and the compression start angle β2 of the compression space S2 can be set large. Therefore, the compression efficiency of the compressor 2 is further improved, and expansion of the compression mechanism section 18 is suppressed.

Furthermore, the refrigeration cycle device 1 and the compressor 2 according to the present embodiment include a compression mechanism section 18 having a partition plate 56 provided between the low pressure side cylinder 55 and the high pressure side cylinder 57 of the compression mechanism section 18. . The partition plate 56 and the high pressure side cylinder 57 have an intermediate pressure passage 75. The intermediate pressure passage 75 connects the low pressure side discharge section 69 of the low pressure side compression chamber 61 and the high pressure side suction section 71 of the high pressure side compression chamber 62. Therefore, expansion of the compression mechanism section 18 is suppressed by efficiently providing the intermediate pressure flow path 75.

Furthermore, the partition plate 56 of the refrigeration cycle device 1 and the compressor 2 according to the present embodiment includes a first partition plate half body 91 and a second partition plate half body 92 superimposed under the first partition plate half body 91. and has. In the partition plate 56, a part of the medium pressure flow path 75, that is, recesses 91a and 92a are provided on the mating surfaces of the first partition plate half 91 and the second partition plate half 92. Therefore, a part of the intermediate pressure flow path 75 is efficiently formed in the partition plate 56, and the degree of freedom in flow path arrangement is improved. Further, the thickness of the second partition plate half 92 below the part of the medium pressure passage 75 is greater than the thickness of the first partition plate half 91 above the part of the medium pressure passage 75. This optimizes the rigidity of the partition plate 56 and suppresses refrigerant leakage.

In addition, in the refrigeration cycle device 1 and the compressor 2 according to the present embodiment, the medium pressure passage 75 of the partition plate 56 is connected to the discharge part 69 of the low pressure side compression chamber 61, and the medium pressure passage 75 of the high pressure side cylinder is connected to the partition plate 56. 56, and is arranged outside the high pressure side compression chamber 62. Therefore, expansion of the compression mechanism section 18 is suppressed by efficiently providing the intermediate pressure flow path 75.

Further, the refrigeration cycle device 1 and the compressor 2 according to the present embodiment include an intermediate pipe 13 provided outside the closed container 16. The intermediate pressure flow path 75 is connected to the high pressure side suction section 71 of the high pressure side compression chamber 62 via the intermediate pipe 13. Therefore, the intermediate pressure flow path 75 can be connected to the high pressure side suction portion 71 of the high pressure side compression chamber 62 via the intermediate pipe 13.

Therefore, according to the refrigeration cycle device 1 and the compressor 2 according to the present embodiment, the reliability of the multi-stage compression mechanism section 18 can be prevented from decreasing and the size can be reduced.

Although several embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and their modifications are included within the scope and gist of the invention, as well as within the scope of the invention described in the claims and its equivalents.

1... Refrigeration cycle device, 2... Compressor, 3... Heat radiator, 4... First expansion device, 5... Second expansion device, 6... Heat absorber, 7... Accumulator, 8... First refrigerant piping, 9... Third Two refrigerant pipes, 12... Outlet pipe, 13... Intermediate pipe, 13u... Upstream intermediate pipe, 13m... Midway pipe, 13d... Downstream intermediate pipe, 16... Sealed container, 17... Electric motor section, 18... Compression mechanism section, 19 ...Crankshaft, 21...Main bearing, 21...Main bearing, 22...Sub bearing, 22...Subshaft part, 23...Frame, 26...Body part, 27...Upper head plate, 28...Lower head plate, 31...Discharge pipe, 32 ... terminal block, 35 ... suction end, 36 ... intermediate discharge end, 37 ... intermediate suction end, 38 ... fixture, 39 ... external muffler, 41 ... intercooler, 43 ... stator, 44 ... rotor, 45 ... Lead line, 47... Main shaft part, 48... Eccentric part, 49... Subshaft part, 51... First eccentric part, 52... Second eccentric part, 55... First cylinder, 56... Partition plate, 57... Second cylinder , 59... Fastening member, 61... First compression chamber, 62... Second compression chamber, 63... First roller, 64... Second roller, 65... First blade, 66... Second blade, 68... First suction part , 69...first discharge part, 71...second suction part, 72...second discharge part, 75...medium pressure passage, 76...first discharge valve, 79...high pressure passage, 81...second discharge valve, 82... First discharge muffler, 83... Second discharge muffler, 91... First partition plate half, 91a... Recess, 91b... Hole, 92... Second partition plate half, 92a... Recess, 92b... Hole, 101... Second External muffler, 104, 104e, 104f, 104g...groove, d1, d2...outer diameter dimension, D1, D2...inner diameter dimension, S1...suction space, S2...compression space, t1, t2...thickness.

Claims (8)

1. an airtight container having a central axis extending in the vertical direction;
   an electric motor section provided in the sealed container;
   a low-pressure side eccentric part that is eccentric from the central axis of the sealed container by a first eccentric length; and a high-pressure side eccentric part that is provided below the low-pressure side eccentric part and is eccentric from the central axis by a second eccentric length. and a crankshaft that is rotationally driven about the central shaft by the electric motor section;
   a low-pressure side cylinder having a low-pressure side compression chamber that compresses and discharges the introduced gaseous refrigerant using the power of the low-pressure side eccentric part; A compression mechanism section having a high pressure side cylinder having a high pressure side compression chamber that is compressed by power, and a partition plate provided between the low pressure side cylinder and the high pressure side cylinder,
   The height of the low pressure side compression chamber is the same as the height of the high pressure side compression chamber,
   The rotary compressor has an inner diameter dimension of the low pressure side compression chamber that is larger than an inner diameter dimension of the high pressure side compression chamber.
2. The rotary compressor according to claim 1, wherein the first eccentric length is greater than the second eccentric length.
3. The rotary compressor according to claim 1 or 2, wherein a compression start angle of the high pressure side compression chamber is larger than a compression start angle of the low pressure side compression chamber.
4. The rotary compressor according to any one of claims 1 to 3, wherein the high-pressure side cylinder has a groove that is provided on a wall surface that partitions the high-pressure side compression chamber and connects to a suction section of the high-pressure side compression chamber.
5. The partition plate and the high pressure side cylinder have an intermediate pressure flow path,
   The rotary compressor according to any one of claims 1 to 4, wherein the intermediate pressure flow path connects a discharge part of the low pressure side compression chamber and a suction part of the high pressure side compression chamber.
6. The partition plate includes a first partition plate half, and a second partition plate half stacked below the first partition plate half, and the first partition plate half and the second partition plate half are separated from each other. A part of the medium pressure flow path is provided on the mating surface of the plate halves,
   The rotary type according to claim 5, wherein the thickness of the second partition plate half below the part of the medium pressure flow path is greater than the thickness of the first partition plate half above the part of the medium pressure flow path. compressor.
7. comprising an intermediate pipe provided outside the sealed container,
   The rotary compressor according to claim 5 or 6, wherein the intermediate pressure flow path is connected to the suction part of the high pressure side compression chamber via the intermediate piping.
8. A rotary compressor according to any one of claims 1 to 7,
   radiator and
   an expansion device;
   a heat absorber;
   A refrigeration cycle device comprising: the rotary compressor, the radiator, the expansion device, and a refrigerant pipe that connects the heat absorber and allows the refrigerant to flow.
   

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