WO2019171540A1 - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

This rotary compressor is provided with a compression mechanism section which is lubricated by lubricating oil. The compression mechanism section includes: a first bearing and a second bearing, which are arranged at a distance from each other in the axial direction of a hermetic container; a plurality of cylinder bodies disposed between the first bearing and the second bearing and defining a plurality of cylinder chambers; an intermediate partition plate disposed between adjacent cylinder bodies and having a bearing section; and a rotating shaft. The rotating shaft has: a plurality of crank sections positioned between the first bearing and the second bearing and eccentrically rotating within the cylinder chambers; and an intermediate shaft section supported between adjacent crank sections by the bearing section of the intermediate partition plate. The intermediate shaft section is provided between the adjacent crank sections at a position offset toward one crank section, and a gap greater than the thickness of the bearing section of the intermediate partition plate is provided between the other crank section and the intermediate shaft section.

Description

Rotary compressor and refrigeration cycle apparatus

Embodiments of the present invention relate to a multi-cylinder rotary compressor and a refrigeration cycle apparatus including the rotary compressor.

For example, a multi-cylinder rotary compressor used in an air conditioner is provided with a compression mechanism that compresses a refrigerant inside an airtight container.

The compression mechanism includes a plurality of cylinder chambers partitioned by an intermediate partition plate, and a rotating shaft having a plurality of crank portions that can be accommodated in the cylinder chamber, and a roller attached to the outer peripheral surface of the crank portion is eccentric in the cylinder chamber. Rotate. As a result, the volumes of the suction region and the compression region of the cylinder chamber change, and the gas-phase refrigerant sucked into the suction region is compressed.

By the way, there is conventionally known a rotary compressor in which an intermediate shaft portion is provided between two adjacent crank portions of a rotation shaft and the intermediate shaft portion is rotatably supported by an intermediate partition plate. According to this conventional rotary compressor, the shaft runout of the rotating shaft can be suppressed even during high speed operation in which the rotating shaft rotates at high speed.

JP-A-5-312172

In a rotary compressor whose rotating shaft has an intermediate shaft portion, lubricating oil is supplied to the sliding portion between the intermediate shaft portion and the intermediate partition plate in order to reduce friction loss between the intermediate shaft portion and the intermediate partition plate. It has become so. Furthermore, in order to secure a space for temporarily storing lubricating oil between the intermediate shaft portion and the crank portion located on the upper side, the intermediate shaft portion is positioned just in the middle between two adjacent crank portions.

However, according to this configuration, the intermediate shaft portion has a flat disk shape, and it is difficult to ensure a sufficient thickness dimension of the intermediate shaft portion along the axial direction of the rotation shaft. For this reason, the lubricating oil easily flows out between the intermediate shaft portion and the intermediate partition plate, and the lubricating oil film separating the intermediate shaft portion and the intermediate partition plate may be interrupted.

Therefore, solid contact friction that causes poor lubrication occurs between the intermediate shaft portion and the intermediate partition plate, and the performance or reliability of the rotary compressor cannot be denied.

An object of the present invention is to obtain a rotary compressor that can improve the lubricity of an intermediate shaft portion of a rotating shaft and contribute to a reduction in friction loss of a compression mechanism portion.

According to this embodiment, the rotary compressor includes a cylindrical airtight container, a compression mechanism that compresses the refrigerant inside the airtight container and is lubricated with the lubricating oil stored in the airtight container, and the airtight container. And an electric motor that drives the compression mechanism.
The compression mechanism portion is disposed between the first bearing and the second bearing that are spaced apart in the axial direction of the sealed container, and between the first bearing and the second bearing, The airtight containers are arranged at intervals in the axial direction, and each cylinder body defines a cylinder chamber, and the intermediate partition plate interposed between the adjacent cylinder bodies and having a bearing portion, The first journal part supported by the first bearing, the second journal part supported by the second bearing, and positioned between the first journal part and the second journal part A plurality of crank portions rotating eccentrically in the cylinder chamber, and a rotating shaft having an intermediate shaft portion slidably supported by the bearing portion of the intermediate partition plate between the adjacent crank portions.
The intermediate shaft portion of the rotating shaft is provided at a position offset toward one of the crank portions between the adjacent crank portions, and the intermediate partition between the other crank portion and the intermediate shaft portion. A gap larger than the thickness of the bearing portion of the plate is provided.

FIG. 1 is a circuit diagram schematically showing the configuration of the refrigeration cycle apparatus according to the first embodiment. FIG. 2 is a cross-sectional view of the twin rotary compressor according to the first embodiment. FIG. 3 is a cross-sectional view of the compression mechanism portion of the twin rotary compressor in the first embodiment. FIG. 4 is a cross-sectional view schematically showing the positional relationship between a roller and a vane that rotate eccentrically in the first cylinder chamber in the first embodiment. FIG. 5 is a cross-sectional view showing a state in which the second journal portion of the rotating shaft is inserted into the bearing hole of the intermediate partition plate in the first embodiment. FIG. 6 is a cross-sectional view illustrating a state in which the intermediate partition plate is moved between the second crank portion and the intermediate shaft portion of the rotation shaft in the first embodiment. FIG. 7 is a cross-sectional view showing a state in which the intermediate partition plate is shifted in the radial direction of the rotation shaft between the second crank portion and the intermediate shaft portion of the rotation shaft in the first embodiment. FIG. 8 is a cross-sectional view showing a state in which the intermediate shaft portion of the rotating shaft is fitted in the bearing hole of the intermediate partition plate in the first embodiment. FIG. 9 is a cross-sectional view of the compression mechanism portion of the twin rotary compressor according to the second embodiment. FIG. 10 is a cross-sectional view of a triple rotary compressor according to the third embodiment. FIG. 11 is a cross-sectional view of a compression mechanism portion of a triple rotary compressor according to the third embodiment. FIG. 12 is a bottom view of the second intermediate partition plate used in the third embodiment. 13 is a cross-sectional view taken along line F13-F13 in FIG. FIG. 14 is an exploded cross-sectional view showing an outline of the compression mechanism used in the third embodiment. FIG. 15 is a cross-sectional view showing a state in which the second journal portion of the rotating shaft is inserted into the bearing hole of the second intermediate partition plate connected to the second cylinder body in the third embodiment. FIG. 16 is a cross-sectional view showing a state in which the third crank portion of the rotating shaft enters the escape recess of the second intermediate partition plate in the third embodiment. FIG. 17 is a cross-sectional view showing a state in which the bearing hole of the second intermediate partition plate and the intermediate shaft portion of the rotary shaft are coaxially aligned in the third embodiment. FIG. 18 is a cross-sectional view illustrating a state in which the roller is inserted on the first journal portion of the rotation shaft in the third embodiment. FIG. 19 is a cross-sectional view showing a state in which the first intermediate partition plate is overlaid on the second cylinder body mounted on the rotating shaft in the third embodiment. FIG. 20 shows a third embodiment in which the first cylinder body to which the first bearing is connected is overlaid on the first intermediate partition plate, and the spacer is placed on the second journal portion of the rotating shaft. It is sectional drawing which shows the state inserted. FIG. 21 is a cross-sectional view illustrating a state in which a roller is fitted to the outer peripheral surface of the third crank portion of the rotation shaft in the third embodiment. FIG. 22 is a cross-sectional view showing a state where the compression mechanism is assembled in the third embodiment. FIG. 23 is a cross-sectional view of a compression mechanism portion of a triple rotary compressor according to the fourth embodiment.

[First embodiment]
Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 8.

FIG. 1 is a refrigeration cycle circuit diagram of an air conditioner 1 which is an example of a refrigeration cycle apparatus, for example. The air conditioner 1 includes a rotary compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an expansion device 5, and an indoor heat exchanger 6 as main elements. The plurality of elements constituting the air conditioner 1 are connected via a circulation circuit 7 in which the refrigerant circulates.

Specifically, as shown in FIG. 1, the discharge side of the rotary compressor 2 is connected to the first port 3 a of the four-way valve 3. The second port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4. The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via an expansion device 5. The indoor heat exchanger 6 is connected to the third port 3 c of the four-way valve 3. The fourth port 3 d of the four-way valve 3 is connected to the suction side of the rotary compressor 2 via the accumulator 8.

When the air conditioner 1 operates in the cooling mode, the four-way valve 3 is switched so that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, the outdoor heat exchanger in which the high-temperature and high-pressure gas-phase refrigerant compressed by the rotary compressor 2 functions as a radiator (condenser) via the four-way valve 3 Led to 4.

The gas-phase refrigerant led to the outdoor heat exchanger 4 is condensed by heat exchange with the air and changed into a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is reduced in pressure in the process of passing through the expansion device 5 and changed to a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 that functions as a heat absorber (evaporator) and exchanges heat with air in the process of passing through the indoor heat exchanger 6.

As a result, the gas-liquid two-phase refrigerant takes heat from the air, evaporates, and changes to a low-temperature / low-pressure gas-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of vaporization of the liquid phase refrigerant, and is sent to a place to be air-conditioned (cooled) as cold air.

The low-temperature and low-pressure gas-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 8 via the four-way valve 3. If liquid refrigerant that could not evaporate is mixed in the refrigerant, the accumulator 8 separates it into liquid phase refrigerant and gas phase refrigerant. The low-temperature and low-pressure gas-phase refrigerant from which the liquid-phase refrigerant has been separated is sucked into the rotary compressor 2 and is compressed again into a high-temperature and high-pressure gas-phase refrigerant by the rotary compressor 2 and discharged to the circulation circuit 7.

On the other hand, when the air conditioner 1 operates in the heating mode, the four-way valve 3 switches so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. Therefore, the high-temperature and high-pressure gas-phase refrigerant discharged from the rotary compressor 2 is guided to the indoor heat exchanger 6 through the four-way valve 3 and exchanges heat with air passing through the indoor heat exchanger 6. That is, the indoor heat exchanger 6 functions as a condenser.

As a result, the gas-phase refrigerant passing through the indoor heat exchanger 6 is condensed by heat exchange with the air and changed into a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is superheated by heat exchange with the gas-phase refrigerant, and is sent to a place to be air-conditioned (heated) as warm air.

The high-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the expansion device 5 and is reduced in pressure in the process of passing through the expansion device 5 to be changed into a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is led to the outdoor heat exchanger 4 functioning as an evaporator, and evaporates by exchanging heat with air here, and changes to a low-temperature / low-pressure gas-phase refrigerant. The low-temperature and low-pressure gas-phase refrigerant that has passed through the outdoor heat exchanger 4 is sucked into the rotary compressor 2 via the four-way valve 3 and the accumulator 8.

Next, a specific configuration of the rotary compressor 2 used in the air conditioner 1 will be described with reference to FIGS. FIG. 2 discloses a vertical twin rotary compressor 2. As shown in FIG. 2, the twin rotary compressor 2 includes a sealed container 10, an electric motor 11, and a compression mechanism unit 12 as main elements.

The sealed container 10 has a cylindrical peripheral wall 10a and is erected along the vertical direction. A discharge pipe 10 b is provided at the upper end of the sealed container 10. The discharge pipe 10 b is connected to the first port 3 a of the four-way valve 3 through the circulation circuit 7. Furthermore, a lubricating oil I that lubricates the compression mechanism 12 is stored in the lower portion of the sealed container 10.

The electric motor 11 is accommodated in an intermediate portion along the axial direction of the sealed container 10 so as to be positioned above the oil level S of the lubricating oil I. The electric motor 11 is a so-called inner rotor type motor, and includes a stator 13 and a rotor 14. The stator 13 is fixed to the inner surface of the peripheral wall 10 a of the sealed container 10. The rotor 14 is coaxially positioned on the central axis O <b> 1 of the sealed container 10 and is surrounded by the stator 13.

The compression mechanism 12 is accommodated in the lower part of the sealed container 10 so as to be immersed in the lubricating oil I. As shown in FIGS. 2 and 3, the compression mechanism unit 12 includes a first cylinder body 16, a second cylinder body 17, an intermediate partition plate 18, a spacer 19, a first bearing 20, a second bearing 21, and The rotating shaft 22 is provided as a main element.

The first cylinder body 16 and the second cylinder body 17 are separated from each other in the axial direction of the sealed container 10. The intermediate partition plate 18 is interposed between the first cylinder body 16 and the second cylinder body 17. The upper surface of the intermediate partition plate 18 is overlaid on the lower surface of the first cylinder body 16 so as to cover the inner diameter portion of the first cylinder body 16 from below. The lower surface of the intermediate partition plate 18 faces the upper surface of the second cylinder body 17.

The spacer 19 is a flat disk-shaped element, and is interposed between the lower surface of the intermediate partition plate 18 and the upper surface of the second cylinder body 17. The lower surface of the spacer 19 is overlaid on the upper surface of the second cylinder body 17 so as to cover the inner diameter portion of the second cylinder body 17 from above.

The first bearing 20 is positioned on the first cylinder body 16. The first bearing 20 has a flange portion 23 that projects toward the inner surface of the peripheral wall 10 a of the sealed container 10. The flange portion 23 is superimposed on the upper surface of the first cylinder body 16 so as to cover the inner diameter portion of the first cylinder body 16 from above. A region surrounded by the inner diameter portion of the first cylinder body 16, the intermediate partition plate 18 and the flange portion 23 of the first bearing 20 defines a first cylinder chamber 24.

According to the present embodiment, the flange portion 23 of the first bearing 20 is surrounded by the ring-shaped support frame 25. The support frame 25 is fixed to a predetermined position on the inner surface of the peripheral wall 10a of the sealed container 10 by means such as welding.

The lower surface of the support frame 25 is overlaid on the upper surface of the outer peripheral portion of the first cylinder body 16. The outer peripheral portion of the first cylinder body 16 is coupled to the support frame 25 via a plurality of first fastening bolts 26 (only one is shown).

Further, the flange portion 23 of the first bearing 20, the first cylinder body 16, and the intermediate partition plate 18 are stacked on each other in the axial direction of the sealed container 10, and a plurality of second fastening bolts 27 (one Only connected to each other). The first fastening bolts 26 and the second fastening bolts 27 are arranged at intervals in the circumferential direction of the first cylinder chamber 24.

The second bearing 21 is located below the second cylinder body 17. The second bearing 21 has a flange portion 29 that protrudes toward the inner surface of the peripheral wall 10 a of the sealed container 10. The flange portion 29 is superimposed on the lower surface of the second cylinder body 17 so as to cover the inner diameter portion of the second cylinder body 17 from below. A region surrounded by the inner diameter portion of the second cylinder body 17, the spacer 19, and the flange portion 29 of the second bearing 21 defines a second cylinder chamber 30.

The flange portion 29, the second cylinder body 17, the spacer 19, and the intermediate partition plate 18 of the second bearing 21 are stacked on each other in the axial direction of the sealed container 10, and a plurality of third fastening bolts 31 (one (Only one is shown). The third fastening bolts 31 are arranged at intervals in the circumferential direction of the second cylinder chamber 30.

Therefore, the first bearing 20 and the second bearing 21 are arranged with a space in the axial direction of the sealed container 10, and the first bearing 20 and the second bearing 21 are arranged between the first bearing 20 and the second bearing 21. Cylinder body 16, second cylinder body 17, intermediate partition plate 18 and spacer 19 are arranged.

2 and 3, the first cylinder chamber 24 and the second cylinder chamber 30 are connected to the accumulator 8 via suction pipes 32a and 32b constituting the circulation circuit 7, respectively. The gas-phase refrigerant from which the liquid-phase refrigerant has been separated by the accumulator 8 is guided to the first cylinder chamber 24 and the second cylinder chamber 30 through the suction pipes 32a and 32b.

Furthermore, a first discharge muffler 34 is attached to the first bearing 20. A first silencing chamber 35 is formed between the first discharge muffler 34 and the first bearing 20. The first silencing chamber 35 is opened inside the hermetic container 10 through a plurality of exhaust holes (not shown) provided in the first discharge muffler 34.

The second discharge muffler 36 is attached to the second bearing 21. A second silencing chamber 37 is formed between the second discharge muffler 36 and the second bearing 21. The second silencing chamber 37 communicates with the first silencing chamber 35 via a discharge passage (not shown).

As shown in FIG. 2, the rotating shaft 22 is coaxially positioned on the central axis O1 of the sealed container 10. The rotating shaft 22 includes a first journal part 40a, a second journal part 40b, a first crank part 41a, a second crank part 41b, and an intermediate shaft part 42.

2 and 5, the first journal portion 40a is positioned at an intermediate portion along the axial direction of the rotary shaft 22, and is rotatably supported by the first bearing 20. As shown in FIG. One end of the rotating shaft 22 protruding from the first bearing 20 is connected to the rotor 14 of the electric motor 11. The second journal portion 40 b is positioned at the other end portion along the axial direction of the rotary shaft 22 and is rotatably supported by the second bearing 21.

The first crank part 41a and the second crank part 41b are formed integrally with the rotary shaft 22 so as to be positioned between the first journal part 40a and the second journal part 40b. The first and second crank portions 41a and 41b are disk-shaped elements each having a thickness dimension along the axial direction of the rotating shaft 22, and are separated from each other in the axial direction of the rotating shaft 22, and the rotating shaft Eccentric with respect to 22 center line O2. The first crank portion 41 a adjacent to the first journal portion 40 a is located in the first cylinder chamber 24. The second crank portion 41 b adjacent to the second journal portion 40 b is located in the second cylinder chamber 30.

The intermediate shaft portion 42 of the rotary shaft 22 is integrally formed with the rotary shaft 22 so as to be positioned between the adjacent first crank portion 41a and second crank portion 41b. The intermediate shaft portion 42 is a disk-shaped element provided coaxially with the rotary shaft 22, and has a thickness dimension along the axial direction of the rotary shaft 22. The diameter d1 of the intermediate bearing portion 42 is set to be equal to or larger than the diameter d2 of the second crank portion 41b.

3 and 4, a ring-shaped roller 43 is fitted to the outer peripheral surface of the first crank portion 41a. The roller 43 follows the rotation shaft 22 and rotates eccentrically in the first cylinder chamber 24, and a part of the outer peripheral surface of the roller 43 is slidably contacted with the inner peripheral surface of the first cylinder chamber 24. It is supposed to be.

The one end surface of the roller 43 is slidably in contact with the lower surface of the flange portion 23 of the first bearing 20. The other end surface of the roller 43 is slidably in contact with the upper surface of the intermediate partition plate 18. Thereby, the airtightness of the first cylinder chamber 24 is ensured.

A ring-shaped roller 44 is fitted to the outer peripheral surface of the second crank portion 41b. The roller 44 follows the rotation shaft 22 and rotates eccentrically in the second cylinder chamber 30, and a part of the outer peripheral surface of the roller 44 is slidably in line contact with the inner peripheral surface of the second cylinder chamber 30. It is supposed to be.

The one end surface of the roller 44 is slidably in contact with the lower end surface of the spacer 19. The other end surface of the roller 43 is slidably in contact with the upper surface of the flange portion 29 of the second bearing 21. Thereby, the airtightness of the second cylinder chamber 30 is ensured.

As shown schematically in FIG. 4, a vane 47 is accommodated in the vane slot 46 of the first cylinder body 16. The vane 47 is movable in the radial direction of the first cylinder chamber 24 and is biased toward the first cylinder chamber 24 via a spring 48. The tip of the vane 47 is slidably pressed against the outer peripheral surface of the roller 43.

The vane 47 cooperates with the roller 43 to partition the first cylinder chamber 24 into a suction region R1 and a compression region R2. Further, the vane 47 advances into the first cylinder chamber 24 following the eccentric rotation of the roller 43 or reciprocates in the direction away from the first cylinder chamber 24.

As a result, when the roller 43 rotates eccentrically, the volumes of the suction region R1 and the compression region R2 of the first cylinder chamber 24 change, and the gas phase sucked into the suction region R1 of the first cylinder chamber 24 from the suction pipe 32a. The refrigerant is compressed.

Although not shown, the second cylinder chamber 30 is also divided into a suction region and a compression region by a similar vane. Therefore, when the roller 44 rotates eccentrically, the volume of the suction region and the compression region of the second cylinder chamber 30 changes, and the gas-phase refrigerant sucked into the suction region of the second cylinder chamber 30 from the suction pipe 32b is compressed. The

2 and 3, the flange portion 23 of the first bearing 20 is provided with a first discharge valve 50 that is opened and closed by a roller 43 that rotates eccentrically. When the first discharge valve 50 is opened, the gas-phase refrigerant compressed in the first cylinder chamber 24 is discharged into the first silencing chamber 35.

The flange portion 29 of the second bearing 21 is provided with a second discharge valve 51 that is opened and closed by a roller 44 that rotates eccentrically. When the second discharge valve 51 is opened, the gas-phase refrigerant compressed in the second cylinder chamber 30 is guided from the second silencer chamber 37 to the first silencer chamber 35 through the discharge passage. The gas-phase refrigerant compressed in the second cylinder chamber 30 is discharged from the exhaust hole of the first discharge muffler 34 into the sealed container 10.

As shown in FIGS. 3 and 5, the intermediate shaft portion 42 of the rotating shaft 22 is largely displaced toward the first crank portion 41 a side between the adjacent first crank portion 41 a and the second crank portion 41 b. In the position.

Therefore, a first gap C1 along the axial direction of the rotating shaft 22 is formed between the intermediate shaft portion 42 and the first crank portion 41a, and the intermediate shaft portion 42 and the second crank portion 41b are separated from each other. A second gap C2 along the axial direction of the rotary shaft 22 is formed between them.

The first gap C1 is much smaller than the second gap C2. The second gap C2 defines a space SP equivalent to the thickness of the intermediate shaft portion 42 between the intermediate shaft portion 42 and the second crank portion 41b.

3, the intermediate shaft portion 42 of the rotating shaft 22 is supported by the intermediate partition plate 18. The intermediate partition plate 18 of the present embodiment has a thickness that exceeds the intermediate shaft portion 42. For this reason, the lower end portion of the intermediate partition plate 18 protrudes toward the second crank portion 41 b from the intermediate shaft portion 42.

A bearing portion 52 a having a bearing hole 52 and a relief recess 55 are formed at the center of the intermediate partition plate 18. As shown in FIG. 5, the bearing hole 52 has an inner diameter d3 into which the second crank portion 41b can be inserted, and the intermediate shaft portion 42 of the rotary shaft 22 is slidably fitted in the bearing hole 52. Yes. By this fitting, the intermediate partition plate 18 also functions as a bearing that supports the intermediate shaft portion 42.

The sliding part between the intermediate shaft part 42 and the bearing hole 52 is lubricated with the lubricating oil I stored in the sealed container 10. That is, the outer peripheral surface of the intermediate shaft portion 42 and the inner peripheral surface of the bearing hole 52 are separated by an oil film of lubricating oil, and much of the load acting on the intermediate shaft portion 42 when the rotary shaft 22 rotates is oil film reaction. Taken by force.

The escape recess 55 is a circular element continuous to the bearing portion 52a, and is opened on the lower surface of the intermediate partition plate 18. The escape recess 55 has an inner diameter d4 larger than the bearing hole 52 and is eccentric with respect to the bearing hole 52.

Further, the thickness t1 of the bearing portion 52a of the intermediate partition plate 18 extending from the bottom of the escape recess 55 to the upper surface of the intermediate partition plate 18 is the second clearance C2 between the intermediate shaft portion 42 and the second crank portion 41b. Is set to be slightly smaller. In other words, the second gap C2 is larger than the thickness t1 of the bearing portion 52a of the intermediate partition plate 18.

A circular communication hole 56 is formed at the center of the spacer 19. The communication hole 56 is continuous with the escape recess 55 and has a size that allows the second crank portion 41b of the rotary shaft 22 to be inserted therethrough. A portion located between the intermediate shaft portion 42 of the rotating shaft 22 and the other crank portion 41 b passes through the escape recess 55 of the intermediate partition plate 18 and the communication hole 56 of the spacer 19.

Next, the procedure for assembling the compression mechanism 12 will be described with reference to FIGS.

First, as shown in FIG. 5, the second journal portion 40 b of the rotary shaft 22 is inserted into the bearing hole 52 and the relief recess 55 of the bearing portion 52 a of the intermediate partition plate 18.

In this state, as shown in FIG. 6, the intermediate partition plate 18 is moved in the axial direction of the rotary shaft 22 so that the second crank portion 41 b passes through the bearing hole 52. Accordingly, a portion located between the intermediate shaft portion 42 of the rotating shaft 22 and the second crank portion 41 b is positioned inside the bearing hole 52, and a part of the second crank portion 41 b is escaped from the recess 55. Get in. Since the escape recess 55 is eccentric with respect to the bearing hole 52, a gap g along the radial direction of the second crank portion 41b is formed between a part of the inner peripheral portion of the escape recess 55 and the second crank portion 41b. Is secured.

Next, as shown in FIG. 7, the intermediate partition plate 18 is moved in the radial direction of the rotary shaft 22 so that the second crank portion 41 b enters the gap g, and the bearing hole 52 and the rotary shaft 22 of the intermediate partition plate 18 are moved. The intermediate shaft portion 42 is coaxially positioned.

Thereafter, as shown in FIG. 8, the intermediate partition plate 18 is moved in the axial direction of the rotary shaft 22, and the intermediate shaft portion 42 of the rotary shaft 22 is slidably fitted into the bearing hole 52 of the intermediate partition plate 18. . By this fitting, the intermediate shaft portion 42 of the rotating shaft 22 is supported by the bearing portion 52a of the intermediate partition plate 18, and the intermediate partition plate 18 functions as a bearing.

Although not shown, the roller 43 is subsequently guided from the direction of one end of the rotary shaft 22 through the outside of the rotary shaft 22 onto the intermediate partition plate 42, and the roller 43 protrudes from the intermediate partition plate 42. Is fitted to the outer peripheral surface of the crank portion 41a. Further, the first cylinder body 16 is superposed on the intermediate partition plate 18, and the roller 43 is accommodated in the inner diameter portion of the first cylinder body 16.

Next, the first bearing 20 is fitted into the first journal portion 40 a of the rotating shaft 22, and the flange portion 23 of the first bearing 20 is overlaid on the upper surface of the first cylinder body 16. In this state, the flange portion 23 of the first bearing 20, the first cylinder body 16 and the intermediate partition plate 18 are integrally coupled together with the first discharge muffler 34 by the second fastening bolts 27.

Next, the second journal portion 40 b of the rotary shaft 22 is inserted into the communication hole 56 of the spacer 19, and the spacer 19 is moved in the axial direction of the rotary shaft 22 so that the second crank portion 41 b passes through the communication hole 56. Let Accordingly, the spacer 19 overlaps the lower surface of the intermediate partition plate 18 so that the communication hole 56 of the spacer 19 matches the escape recess 55 of the intermediate partition plate 18.

Subsequently, the roller 44 is fitted to the outer peripheral surface of the second crank portion 41b of the rotating shaft 22 protruding from the intermediate partition plate 42 through the outside of the second journal portion 40b. Further, the second cylinder body 17 is overlaid on the spacer 19, and the roller 44 is accommodated in the inner diameter portion of the second cylinder body 17.

Next, the second bearing 21 is fitted into the second journal portion 40 b of the rotating shaft 22, and the flange portion 29 of the second bearing 21 is overlapped with the lower surface of the second cylinder body 17. In this state, the flange portion 29 of the second bearing 21, the second cylinder body 17, the spacer 19, and the intermediate partition plate 18 are integrally coupled together with the second discharge muffler 36 by the third fastening bolt 31. Thereby, a series of assembly work of the compression mechanism part 12 is completed.

According to the first embodiment, the rotating shaft 22 that rotates the rollers 43 and 44 eccentrically has the intermediate shaft portion 42 that is located between the adjacent first crank portion 41a and the second crank portion 41b. The intermediate shaft portion 42 is slidably fitted in the bearing hole 52 of the intermediate partition plate 18.

Therefore, the rotary shaft 22 can be supported even at an intermediate position between the first bearing 20 and the second bearing 21. As a result, for example, the rotary shaft 22 and the first bearing 20 and the first bearing 20 are caused by the pressure of the gas-phase refrigerant compressed in the first cylinder chamber 24 and the second cylinder chamber 30 and the inertial force of the rotary shaft 22 rotating at high speed. Even if the second bearing 21 is bent from the starting point, the bending of the rotating shaft 22 can be suppressed by the intermediate partition plate 18.

Therefore, the shaft runout of the rotating shaft 22 and local wear of the rollers 43 and 44 due to the shaft runout can be prevented, and the high-performance and highly reliable twin rotary compressor 2 can be obtained.

Furthermore, according to the present embodiment, the intermediate shaft portion 42 of the rotating shaft 22 is largely offset toward the first crank portion 41a with respect to the second crank portion 41b, and therefore the first cylinder body 16 and the roller 43 There is no need to increase the height dimension. In addition, since the first gap C1 is provided between the intermediate shaft portion 42 and the first crank portion 41a, the workability of the rotating shaft 22 is not deteriorated.

Moreover, since the second gap C2 between the intermediate shaft portion 42 and the second crank portion 41b is larger than the thickness t1 of the bearing portion 52a of the intermediate partition plate 18, the assembly of the compression mechanism portion 12 is performed. The thickness of the intermediate shaft portion 42 along the axial direction of the rotary shaft 22 and the length of the bearing hole 52 of the intermediate partition plate 18 can be sufficiently ensured without impairing the performance.

As a result, in comparison with the prior art, it is difficult for the lubricating oil to flow out between the intermediate shaft portion 42 and the bearing hole 52, and the lubrication separating the outer peripheral surface of the intermediate shaft portion 42 and the inner peripheral surface of the bearing hole 52 is performed. It is possible to prevent the oil film of oil from being interrupted. Therefore, the lubricity of the intermediate shaft portion 42 of the rotating shaft 22 can be improved, the friction loss of the compression mechanism portion 12 can be suppressed as much as possible, and the performance and reliability of the twin rotary compressor 2 can be enhanced.

[Second Embodiment]
FIG. 9 discloses a second embodiment. The second embodiment is different from the first embodiment in the configuration of a part of the compression mechanism unit 12. Other basic configurations of the twin rotary compressor 2 are the same as those in the first embodiment.

As shown in FIG. 9, according to the compression mechanism portion 12 of the second embodiment, the intermediate partition plate 60 that rotatably supports the intermediate shaft portion 42 of the rotating shaft 22 includes the intermediate shaft portion 42 and the second crank portion. It has a thickness t2 equivalent to that of the intermediate shaft portion 42 so as not to overhang the space SP between the intermediate shaft portion 41b. Therefore, the intermediate partition plate 60 of the second embodiment is thinner than the intermediate partition plate 18 of the first embodiment.

As the intermediate partition plate 60 becomes thinner, the thickness of the spacer 61 interposed between the intermediate partition plate 60 and the second cylinder body 17 increases conversely. That is, the spacer 61 has a thickness t3 that approaches the space SP between the intermediate shaft portion 42 and the second crank portion 41b. Therefore, the length of the communication hole 56 of the spacer 61 along the axial direction of the rotating shaft 22 is increased, and the communication hole 56 is in close communication with the bearing hole 52 of the intermediate partition plate 60.

In the second embodiment, when the compression mechanism portion 12 is assembled, the second journal portion 40 b of the rotating shaft 22 is inserted into the bearing hole 52 of the intermediate partition plate 60, and the second crank portion 41 b is inserted into the bearing hole 52. The intermediate partition plate 60 is moved in the axial direction of the rotary shaft 22 so as to pass through. By this movement, the intermediate partition plate 60 is positioned between the intermediate shaft portion 42 and the second crank portion 41b.

Next, the position of the intermediate partition plate 60 with respect to the rotary shaft 22 is adjusted so that the bearing hole 52 of the intermediate partition plate 60 is positioned coaxially with the intermediate shaft portion 42 of the rotary shaft 22. Thereafter, the intermediate partition plate 60 is moved in the axial direction of the rotary shaft 22, so that the intermediate shaft portion 42 of the rotary shaft 22 is slidably fitted in the bearing hole 52 of the intermediate partition plate 60. By this fitting, the intermediate shaft portion 42 of the rotating shaft 22 is supported by the intermediate partition plate 60, and the intermediate partition plate 60 functions as a bearing.

Also in the second embodiment, the thickness of the intermediate shaft portion 42 along the axial direction of the rotating shaft 22, the thickness of the bearing portion 52 a of the intermediate partition plate 60, and the length of the bearing hole 52 are sufficiently ensured. be able to. Therefore, similarly to the first embodiment, it is possible to prevent the oil film of the lubricating oil separating the outer peripheral surface of the intermediate shaft portion 42 and the inner peripheral surface of the bearing hole 52 from being interrupted, and the intermediate shaft portion 42 of the rotary shaft 22. The lubricity can be improved.

Further, when the compression mechanism portion 12 is assembled, the intermediate partition plate 60 is easily moved from the second journal portion 40b side of the rotary shaft 22 toward the intermediate shaft portion 42 by the amount of the thin intermediate partition plate 60. Can be moved.

[Third embodiment]
10 to 22 disclose a third embodiment. The third embodiment discloses a triple rotary compressor 70 having three cylinder bodies. The triple rotary compressor 70 is different from the first embodiment in the configuration of the compression mechanism unit 71 accommodated in the sealed container 10. The other configuration of the triple rotary compressor 70 is basically the same as that of the twin rotary compressor 2 of the first embodiment. Therefore, in the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

As shown in FIG. 10, the compression mechanism 71 includes a first cylinder body 72, a second cylinder body 73, a third cylinder body 74, a first intermediate partition plate 75, a second intermediate partition plate 76, The spacer 77 and the rotating shaft 78 are provided as main elements.

The first to third cylinder bodies 72, 73, 74 are arranged at intervals in the axial direction of the sealed container 10. The first intermediate partition plate 75 is interposed between the first cylinder body 72 and the second cylinder body 73. The upper surface of the first intermediate partition plate 75 is overlaid on the lower surface of the first cylinder body 72 so as to cover the inner diameter portion of the first cylinder body 72 from below. The lower surface of the first intermediate partition plate 75 is overlaid on the upper surface of the second cylinder body 73 so as to cover the inner diameter portion of the second cylinder body 73 from above.

Furthermore, a through hole 75 a is formed in the center of the first intermediate partition plate 75. The through hole 75 a is located between the inner diameter portion of the first cylinder body 72 and the inner diameter portion of the second cylinder body 73.

The second intermediate partition plate 76 is interposed between the second cylinder body 73 and the third cylinder body 74. The upper surface of the second intermediate partition plate 76 is overlaid on the lower surface of the second cylinder body 73 so as to cover the inner diameter portion of the second cylinder body 73 from below. The lower surface of the second intermediate partition plate 76 faces the upper surface of the third cylinder body 74.

The spacer 77 is a flat disk-shaped element, and is interposed between the lower surface of the second intermediate partition plate 76 and the upper surface of the third cylinder body 74. The upper surface of the spacer 77 is overlapped with the lower surface of the second intermediate partition plate 76. The lower surface of the spacer 77 is overlaid on the upper surface of the third cylinder body 74 so as to cover the inner diameter portion of the third cylinder body 74 from above.

The first bearing 20 similar to that of the first embodiment is positioned on the first cylinder body 72. The flange portion 23 of the first bearing 20 is overlaid on the upper surface of the first cylinder body 72 so as to cover the inner diameter portion of the first cylinder body 72 from above. A region surrounded by the inner diameter portion of the first cylinder body 72, the first intermediate partition plate 75, and the flange portion 23 of the first bearing 20 defines a first cylinder chamber 80.

The area surrounded by the inner diameter portion of the second cylinder body 73, the first intermediate partition plate 75 and the second intermediate partition plate 76 defines a second cylinder chamber 81.

Further, the flange portion 23 of the first bearing 20, the first cylinder body 72, the first intermediate partition plate 75, the second cylinder body 73, and the second intermediate partition plate 76 are arranged in the axial direction of the sealed container 10. They are stacked on one another and are integrally coupled via a plurality of second fastening bolts 27 (only one is shown).

The second bearing 21 similar to that of the first embodiment is located under the third cylinder body 74. The flange portion 29 of the second bearing 21 is overlaid on the lower surface of the third cylinder body 74 so as to cover the inner diameter portion of the third cylinder body 74 from below. A region surrounded by the inner diameter portion of the third cylinder body 74, the spacer 77 and the flange portion 29 of the second bearing 21 defines a third cylinder chamber 82.

The flange portion 29, the third cylinder body 74, the spacer 77, and the second intermediate partition plate 76 of the second bearing 21 are stacked on each other in the axial direction of the sealed container 10, and include a plurality of third fastening bolts. 31 (only one is shown).

Therefore, in the present embodiment, the first to third cylinder bodies 72, 73, 74, the first intermediate partition plate 75, and the second intermediate partition are provided between the first bearing 20 and the second bearing 21. Plates 76 and spacers 77 are alternately arranged.

As shown in FIGS. 10 and 11, the first cylinder chamber 80 is connected to the accumulator 8 via the suction pipe 32a. The second cylinder chamber 81 and the third cylinder chamber 82 are connected to the accumulator 8 via the second intermediate partition plate 76 and the suction pipe 32b.

A specific configuration of the second intermediate partition plate 76 will be described with reference to FIGS. 11 to 13. 12 is a bottom view of the second intermediate partition plate 76 as viewed from the third cylinder body 74 side, and FIG. 13 is a cross-sectional view taken along line F13-F13 of FIG.

As shown in FIGS. 11 to 13, a joint portion 83 is formed on a part of the outer peripheral portion of the second intermediate partition plate 76. The joint portion 83 projects from the outer peripheral portion of the second intermediate partition plate 76 toward the peripheral wall 10 a of the sealed container 10. Inside the joint portion 83, there are formed a suction port 84 to which a suction pipe 32b extending from the accumulator 8 is connected, and two branch passages 85a and 85b branched in a bifurcated manner from the downstream end of the suction port 84. Yes.

The suction port 84 is opened at the protruding end of the joint portion 83 and extends from the protruding end toward the center of the second intermediate partition plate 76. One branch passage 85 a is opened on the upper surface of the second intermediate partition plate 76 so as to communicate with the second cylinder chamber 81. The other branch passage 85 b is opened on the lower surface of the second intermediate partition plate 76 so as to face the third cylinder chamber 82.

The second intermediate partition plate 76 incorporating the suction port 84 and the two branch passages 85a and 85b has an increased thickness along the axial direction of the sealed container 10, and the first to third cylinder bodies 72 and 73 are provided. , 74 thicker.

Further, as shown in FIG. 12, the second intermediate partition plate 76 has through holes 86 a and 86 b that are part of a pair of discharge passages connecting the first silencing chamber 35 and the second silencing chamber 37. have. The through holes 86 a and 86 b are separated from each other in the circumferential direction of the second intermediate partition plate 76.

As shown in FIG. 10, the rotation shaft 78 is coaxially positioned on the central axis O <b> 1 of the sealed container 10. The rotating shaft 78 has a first journal portion 87 a, a second journal portion 87 b, first to third crank portions 88 a, 88 b, 88 c and an intermediate shaft portion 89.

As shown in FIGS. 10 and 14, the first journal portion 87a is positioned at an intermediate portion along the axial direction of the rotating shaft 78, and is rotatably supported by the first bearing 20. One end of the rotating shaft 78 protruding from the first bearing 20 is connected to the rotor 14 of the electric motor 11. The second journal portion 87 b is positioned at the other end portion along the axial direction of the rotation shaft 78 and is rotatably supported by the second bearing 21.

The first to third crank portions 88a, 88b, 88c are formed integrally with the rotary shaft 78 so as to be positioned between the first journal portion 87a and the second journal portion 87b. The first to third crank portions 88a, 88b, 88c are disk-shaped elements each having a thickness dimension along the axial direction of the rotating shaft 78, and are separated from each other in the axial direction of the rotating shaft 78. It is eccentric with respect to the center line O2 of the rotating shaft 22.

The first crank portion 88a is located in the first cylinder chamber 80. The second crank portion 88 b is located in the second cylinder chamber 81. The third crank portion 88 c is located in the third cylinder chamber 82. Further, the portion of the rotating shaft 78 located between the first crank portion 88 a and the second crank portion 88 b passes through the through hole 75 a of the first intermediate partition plate 75.

As shown in FIGS. 11 and 14, the intermediate shaft portion 89 of the rotating shaft 78 is formed integrally with the rotating shaft 78 so as to be positioned between the adjacent second crank portion 88b and the third crank portion 88c. Has been. The intermediate shaft portion 89 is a disk-shaped element provided coaxially with the rotation shaft 78 and has a thickness dimension along the axial direction of the rotation shaft 78. The diameter d5 of the intermediate shaft portion 89 is equal to or greater than the diameter d6 of the third crank portion 88c.

In the present embodiment, in order to reduce the friction loss of the compression mechanism portion 71, the diameter d5 of the intermediate shaft portion 89 is set smaller than the diameter d7 of the first crank portion 88a and the diameter d8 of the second crank portion 88b. Yes. Furthermore, the diameter d9 of the second journal portion 87b is also set smaller than the diameter d10 of the first journal portion 87a.

A ring-shaped roller 91 is fitted to the outer peripheral surface of the first crank portion 88a. The roller 91 follows the rotation shaft 78 and rotates eccentrically in the first cylinder chamber 80, and part of the outer peripheral surface of the roller 91 is slidably in line contact with the inner peripheral surface of the first cylinder chamber 80. It is supposed to be.

One end surface of the roller 91 is slidably in contact with the lower surface of the flange portion 23 of the first bearing 20. The other end surface of the roller 91 is slidably in contact with the upper surface of the first intermediate partition plate 75. Thereby, the airtightness of the first cylinder chamber 80 is ensured.

A ring-shaped roller 92 is fitted to the outer peripheral surface of the second crank portion 88b. The roller 92 follows the rotating shaft 78 and rotates eccentrically in the second cylinder chamber 81, and a part of the outer peripheral surface of the roller 92 is slidably in line contact with the inner peripheral surface of the second cylinder chamber 81. It is supposed to be.

One end surface of the roller 92 is slidably in contact with the lower surface of the first intermediate partition plate 75. The other end surface of the roller 92 is slidably in contact with the upper surface of the second intermediate partition plate 76. Thereby, the airtightness of the second cylinder chamber 81 is ensured.

A ring-shaped roller 93 is fitted to the outer peripheral surface of the third crank portion 88c. The roller 93 follows the rotation shaft 78 and rotates eccentrically in the third cylinder chamber 82, and a part of the outer peripheral surface of the roller 93 is slidably contacted with the inner peripheral surface of the third cylinder chamber 82. It is supposed to be.

The one end surface of the roller 93 is slidably in contact with the lower surface of the spacer 77. The other end surface of the roller 93 is slidably in contact with the upper surface of the flange portion 29 of the second bearing 21. Thereby, the airtightness of the third cylinder chamber 82 is ensured.

The first to third cylinder chambers 80, 81, 82 are divided into a suction area and a compression area by vanes (not shown). Therefore, when the rollers 91, 92, 93 rotate eccentrically in the first to third cylinder chambers 80, 81, 82, the volumes of the suction areas and the compression areas of the cylinder chambers 80, 81, 82 change, and the suction pipes The gas-phase refrigerant sucked into the suction areas of the cylinder chambers 80, 81, 82 from 32a, 32b is compressed.

A first discharge valve 95 that is opened and closed by a roller 91 that rotates eccentrically is provided on the flange portion 23 of the first bearing 20. When the first discharge valve 95 is opened, the gas-phase refrigerant compressed in the first cylinder chamber 80 is guided to the first silencing chamber 35.

The second intermediate valve 75 is provided with a second discharge valve 96 that is opened and closed by a roller 92 that rotates eccentrically. When the second discharge valve 96 is opened, the gas-phase refrigerant compressed in the second cylinder chamber 81 enters the first silencing chamber 35 via a discharge passage (not shown) provided in the first cylinder body 72. Led.

A third discharge valve 97 that is opened and closed by a roller 93 that rotates eccentrically is provided on the flange portion 29 of the second bearing 21. When the third discharge valve 97 is opened, the gas-phase refrigerant compressed in the second cylinder chamber 82 is guided from the second silencer chamber 37 to the first silencer chamber 35 through the discharge passage.

The gas-phase refrigerant compressed in the first to third cylinder chambers 80, 81, 82 merges in the first silencing chamber 35 and is discharged into the sealed container 10 from the exhaust hole of the first discharge muffler 34. Is done.

As shown in FIGS. 10 and 14, the intermediate shaft portion 89 of the rotating shaft 78 is largely offset toward the second crank portion 88 b between the adjacent second crank portion 88 b and the third crank portion 88 c. It is provided at the position. For this reason, a first gap C1 is formed between the intermediate shaft portion 89 and the second crank portion 88b, along the axial direction of the rotary shaft 78, and between the intermediate shaft portion 89 and the third crank portion 88c. A second gap C <b> 2 is formed along the axial direction of the rotation shaft 78.

The first gap C1 is much smaller than the second gap C2. The second gap C2 defines a space SP equivalent to the thickness of the intermediate shaft portion 89 along the axial direction of the rotating shaft 78 between the intermediate shaft portion 89 and the third crank portion 88c.

The intermediate shaft portion 89 of the rotary shaft 78 is supported by the second intermediate partition plate 76. According to the present embodiment, the second intermediate partition plate 76 includes the suction port 84 and the branch passages 85a and 85b, and thus has a thickness that exceeds the intermediate shaft portion 89. For this reason, the lower end portion of the second intermediate partition plate 76 projects from the intermediate shaft portion 89 toward the third crank portion 88c.

A bearing portion 98a having a bearing hole 98 and a relief recess 100 are formed in the central portion of the second intermediate partition plate 76. The bearing hole 98 has an inner diameter d3 into which the third crank portion 88c can be inserted, and an intermediate shaft portion 89 of the rotary shaft 78 is slidably fitted into the bearing hole 98. By this fitting, the second intermediate partition plate 76 also functions as a bearing that supports the intermediate shaft portion 89.

The sliding part between the intermediate shaft part 89 and the bearing hole 98 is lubricated with the lubricating oil I stored in the sealed container 10. Specifically, the outer peripheral surface of the intermediate shaft portion 89 and the inner peripheral surface of the bearing hole 98 are separated by an oil film of lubricating oil, and much of the load acting on the intermediate shaft portion 89 when the rotary shaft 78 rotates. Is received by the oil film reaction force.

As shown in FIG. 12, the relief recess 100 is a circular element continuous to the bearing portion 98 a and is opened on the lower surface of the second intermediate partition plate 76. The escape recess 100 has an inner diameter d4 larger than the bearing hole 98 and is eccentric with respect to the bearing hole 98.

Further, the thickness t1 of the bearing portion 98a from the bottom of the escape recess 100 to the upper surface of the second intermediate partition plate 76 is larger than the second gap C2 between the intermediate shaft portion 89 and the third crank portion 88c. It is set slightly smaller. In other words, the second gap C2 is larger than the thickness t1 of the bearing portion 98a of the second intermediate partition plate 76.

12 and 13, in this embodiment, the opening end of the relief recess 100 and the opening end of the other branch passage 85b are positioned side by side on the lower surface of the second intermediate partition plate 76. The escape recess 100 is eccentric with respect to the center line O2 of the rotation shaft 78 in a direction away from the opening end of the other branch passage 85b.

Therefore, on the lower surface of the second intermediate partition plate 76, a distance L from the opening end of the other branch passage 85b to the opening end of the escape recess 100 can be secured.

A circular communication hole 101 is formed at the center of the spacer 77. The communication hole 101 is continuous with the relief recess 100 and has a size that allows the third crank portion 88c of the rotating shaft 78 to be inserted therethrough. A portion of the rotating shaft 78 positioned between the intermediate shaft portion 89 and the third crank portion 88 c passes through the relief recess 100 of the second intermediate partition plate 76 and the communication hole 101 of the spacer 77.

Furthermore, the spacer 77 has a refrigerant inlet 102 at a position adjacent to the communication hole 101. The refrigerant introduction port 102 is interposed between the other branch passage 85 b of the second intermediate partition plate 76 and the third cylinder chamber 82.

According to the present embodiment, the escape recess 100 is eccentric in the direction away from the opening end of the other branch passage 85b with respect to the center line O2 of the rotation shaft 78, so that the spacer 77 is superimposed on the lower surface of the second intermediate partition plate 76. In this case, a space between the refrigerant inlet 102 and the communication hole 101 can be secured.

For this reason, when the roller 93 rotates eccentrically in the third cylinder chamber 82, one end surface of the roller 93 is always slidably in contact with the lower surface of the spacer 77 between the refrigerant introduction port 102 and the communication hole 101. Maintain state.

Therefore, although the communication hole 101 and the refrigerant introduction port 102 are opened adjacent to each other on the lower surface of the spacer 77, the airtightness of the third cylinder chamber 82 can be maintained satisfactorily. The leakage of the phase refrigerant can be prevented.

Next, the procedure for assembling the compression mechanism 71 will be described with reference to FIGS. 15 to 22 schematically show the assembly process of the compression mechanism 71.

According to the present embodiment, as shown in FIG. 14, the first cylinder body 72 is connected in advance to the flange portion 23 of the first bearing 20 via two coupling bolts 105a (only one is shown). Yes. By this connection, the first cylinder body 72 and the first bearing 20 are aligned so that the center of the inner diameter portion of the first cylinder body 72 and the center of the first bearing 20 coincide.

The second cylinder body 73 is connected in advance to the second intermediate partition plate 76 via two coupling bolts 105b (only one is shown). By this connection, the second cylinder body 73 and the second intermediate partition plate 76 are arranged so that the center of the inner diameter portion of the second cylinder body 73 and the center of the bearing hole 98 of the second intermediate partition plate 76 coincide with each other. Is centered.

Furthermore, the third cylinder body 74 is connected in advance to the flange portion 29 of the second bearing 21 via two coupling bolts 105c (only one is shown). By this connection, the third cylinder body 74 and the second bearing 21 are aligned so that the center of the inner diameter portion of the third cylinder body 74 coincides with the center of the second bearing 21.

First, as shown in FIG. 15, the second journal portion 87b of the rotating shaft 78 is inserted into the inner diameter portion of the second cylinder body 73, the bearing hole 98 and the relief recess 100 of the second intermediate partition plate 76, and rotated. The third crank portion 88 c of the shaft 78 is guided to the inner diameter portion of the second cylinder body 73 through the relief recess 100 and the bearing hole 98 of the second intermediate partition plate 76.

Subsequently, as shown in FIG. 16, the second intermediate partition plate 76 to which the second cylinder body 73 is connected is arranged so that the third crank portion 88 c enters the escape recess 100 of the second intermediate partition plate 76. It is moved in the axial direction of the rotary shaft 78.

Thereby, the intermediate shaft portion 89 and the second crank portion 88b enter the inner diameter portion of the second cylinder body 73. Furthermore, since the relief recess 100 is eccentric with respect to the bearing hole 98, it extends along the radial direction of the third crank portion 88c between a part of the inner peripheral portion of the relief recess 100 and the third crank portion 88c. A gap g is secured.

Next, as shown in FIG. 17, the second intermediate partition plate 76 to which the second cylinder body 73 is connected is moved in the radial direction of the rotary shaft 78 so that the third crank portion 88c enters the gap g. Thus, the bearing hole 98 of the second intermediate partition plate 76 and the intermediate shaft portion 89 of the rotating shaft 78 are positioned coaxially.

Thereafter, as shown in FIG. 18, the second intermediate partition plate 76 connected to the second cylinder body 73 is moved in the axial direction of the rotating shaft 78, and the second intermediate partition plate 76 is inserted into the bearing hole 98. The intermediate shaft part 89 of the rotating shaft 78 is slidably fitted. By this fitting, the intermediate shaft portion 89 of the rotating shaft 78 is supported by the second intermediate partition plate 76, and the second intermediate partition plate 76 functions as a bearing.

Subsequently, as shown in FIG. 18, the roller 92 is guided from the direction of one end of the rotating shaft 78 to the inner diameter portion of the second cylinder body 73 through the outside of the first crank portion 88a, and the roller 92 is guided to the second cylinder. It fits to the outer peripheral surface of the second crank portion 88b located at the inner diameter portion of the body 73.

Next, as shown in FIG. 19, the first intermediate partition plate 75 is superposed on the upper surface of the second cylinder body 73 from the direction of one end portion of the rotating shaft 78 through the outside of the first crank portion 88a. Further, the roller 91 is guided from the direction of one end of the rotating shaft 78 through the outer side of the first journal portion 87a onto the first intermediate partition plate 75, and the roller 91 is fitted to the outer peripheral surface of the first crank portion 88a. Combine.

Next, as shown in FIG. 20, the first cylinder body 72 to which the first bearing 20 is connected is inserted from the direction of one end of the rotation shaft 78 to the outside of the rotation shaft 78, and the first cylinder body 72 is inserted. Is overlapped with the upper surface of the first intermediate partition plate 75. As a result, the roller 91 is positioned on the inner diameter portion of the first cylinder body 72 and the first journal portion 87 a of the rotating shaft 78 is fitted to the first bearing 20.

In this state, the second intermediate partition plate 76, the second cylinder body 73, the first intermediate partition plate 75, the first cylinder body 72, and the flange portion 23 of the first bearing 20 are connected to the first discharge muffler 34. At the same time, the bolts 27 are integrally coupled together.

Next, as shown in FIG. 20, the second journal portion 87 b of the rotating shaft 78 is inserted into the communication hole 101 of the spacer 77, and the spacer 77 is rotated so that the third crank portion 88 c passes through the communication hole 101. It is moved in the axial direction of the shaft 78. As a result, the spacer 77 overlaps the lower surface of the second intermediate partition plate 76 so that the communication hole 101 of the spacer 77 matches the relief recess 100 of the second intermediate partition plate 76.

In a state where the communication hole 101 of the spacer 77 is aligned with the relief recess 100 of the second intermediate partition plate 76, the coolant introduction port 102 of the spacer 77 is the other branch of the second intermediate partition plate 76 as shown in FIG. 11. It matches the passage 85b.

Subsequently, as shown in FIG. 21, the roller 93 is fitted to the outer peripheral surface of the third crank portion 88 c protruding from the spacer 77 through the outside of the second journal portion 87 b of the rotating shaft 78.

Next, as shown in FIG. 22, the third cylinder body 74 to which the second bearing 21 is connected is inserted into the second journal portion 87b of the rotating shaft 78, and the upper surface of the third cylinder body 74 is placed on the spacer. Overlay the bottom of 77. As a result, the roller 93 is positioned on the inner diameter portion of the third cylinder body 74 and the second journal portion 87 b of the rotating shaft 78 is fitted to the second bearing 21.

In this state, the second intermediate partition plate 76, the spacer 77, the third cylinder body 74, and the flange portion 29 of the second bearing 21 are integrally coupled together with the second discharge muffler 36 by the third fastening bolt 31. To do. Thereby, a series of assembly work of the compression mechanism 71 is completed.

According to the third embodiment, the rotating shaft 78 that rotates the rollers 91, 92, and 93 eccentrically has the intermediate shaft portion 89 positioned between the adjacent second crank portion 88b and the third crank portion 88c. The intermediate shaft portion 89 is slidably fitted into the bearing hole 98 of the second intermediate partition plate 76.

Therefore, the rotary shaft 78 can be supported even at an intermediate position between the first bearing 20 and the second bearing 21. As a result, for example, the rotary shaft 78 and the first bearing 20 and the first bearing 20 due to the pressure of the gas-phase refrigerant compressed in the first to third cylinder chambers 80, 81, 82 and the inertial force of the rotary shaft 78 rotating at high speed. Even if the second bearing 21 is bent as a starting point, the second intermediate partition plate 76 can suppress the bending of the rotating shaft 78.

Therefore, the shaft runout of the rotating shaft 78 and the local wear of the rollers 91, 92, 93 due to the shaft runout can be prevented, and the high performance and highly reliable triple rotary compressor 70 can be provided.

Further, according to the present embodiment, the intermediate shaft portion 89 of the rotating shaft 78 is largely offset toward the second crank portion 88b with respect to the third crank portion 88c, and the intermediate shaft portion 89 and the second crank portion are The first gap C1 between the intermediate shaft portion 89 and the third crank portion 88c is much smaller than the first gap C1 between the intermediate shaft portion 89 and the third crank portion 88c.

Moreover, since the second gap C2 is formed to be larger than the thickness of the bearing portion 98a of the second intermediate partition plate 76, the second gap C2 is formed in the axial direction of the rotating shaft 78 without impairing the assembling property of the compression mechanism portion 71. It is possible to sufficiently ensure the thickness of the intermediate shaft portion 89 along and the length of the bearing hole 98 of the second intermediate partition plate 76.

As a result, in comparison with the prior art, it is difficult for the lubricating oil to flow out between the intermediate shaft portion 89 and the bearing hole 98, and the lubrication separating the outer peripheral surface of the intermediate shaft portion 89 and the inner peripheral surface of the bearing hole 98 is performed. It is possible to prevent the oil film of oil from being interrupted. Therefore, the lubricity of the intermediate shaft part 89 of the rotating shaft 78 can be improved, the friction loss of the compression mechanism part 71 can be suppressed as much as possible, and the performance and reliability of the triple rotary compressor 70 can be enhanced.

In addition, since the second intermediate partition plate 76 of the present embodiment incorporates the suction port 84 and the branch passages 85a and 85b, the thickness is larger than that of the intermediate shaft portion 98 of the rotating shaft 78, and its lower end. The portion protrudes into a space SP between the intermediate shaft portion 98 and the third crank portion 88c.

At this time, in this embodiment, a relief recess 100 is formed on the lower surface of the second intermediate partition plate 76, and the relief recess 100 has an inner diameter d 4 larger than the bearing hole 98 and is eccentric with respect to the bearing hole 98. Yes. That is, as best shown in FIGS. 16 and 17, when the third crank portion 88c enters the escape recess 100, a part of the inner peripheral portion of the escape recess 100 and the third crank portion 88c In the meantime, a gap g is secured along the radial direction of the third crank portion 88c.

For this reason, the second intermediate partition plate 76 is moved in the radial direction of the rotary shaft 78 so that the third crank portion 88c enters the gap g, whereby the bearing hole 98 and the rotary shaft of the second intermediate partition plate 76 are moved. The 78 intermediate shaft portions 89 can be coaxially positioned.

Therefore, an intermediate shaft portion 89 is provided between the second crank portion 88b and the third crank portion 88c integrated with the rotary shaft 78, and the intermediate shaft portion 89 is used as a bearing for the second intermediate partition plate 76. The hole 98 can be rotatably supported.

Therefore, the rotating shaft 78 having the first to third crank portions 88a, 88b, 88c and the intermediate shaft portion 89 can be formed as an integral structure, and the number of parts can be reduced in comparison with the assembly-type rotating shaft. At the same time, the number of assembling steps for the compression mechanism 71 can be reduced.

Furthermore, not only the strength of the rotating shaft 78 is improved, but also the balance of the rotating shaft 78 is improved, and there is an advantage that it contributes to the reduction of vibration of the compression mechanism section 71.

[Fourth Embodiment]
FIG. 23 discloses a fourth embodiment. The fourth embodiment is different from the third embodiment in the configuration of a part of the compression mechanism unit 71. The other basic configuration of the triple rotary compressor 70 is the same as that of the third embodiment.

As shown in FIG. 23, in the fourth embodiment, the flow path for distributing the gas-phase refrigerant from the second intermediate partition plate 76 to the second cylinder chamber 81 and the third cylinder chamber 82 is eliminated. Compared with the third embodiment, the second intermediate partition plate 76 is thin and compact.

Specifically, the second intermediate partition plate 76 has a thickness t4 equivalent to that of the intermediate shaft portion 89 so as not to protrude into the space SP between the intermediate shaft portion 89 and the third crank portion 88c. Is formed.

As the second intermediate partition plate 76 becomes thinner, the thickness t5 of the spacer 77 interposed between the second intermediate partition plate 76 and the third cylinder body 74 increases conversely. Therefore, the length of the communication hole 101 of the spacer 77 along the axial direction of the rotating shaft 78 is increased, and the communication hole 101 is directly communicated with the bearing hole 98 of the second intermediate partition plate 76. .

Further, according to the fourth embodiment, the accumulator 8 is removed in accordance with the elimination of the flow path for distributing the gas-phase refrigerant from the second intermediate partition plate 76 to the second cylinder chamber 81 and the third cylinder chamber 82. The suction pipe 32b extending from the pipe has branch pipes 106a and 106b that are bifurcated. The downstream end of one branch pipe 106 a is directly connected to the second cylinder chamber 81 of the second cylinder body 73. The downstream end of the other branch conduit 106 b is directly connected to the third cylinder chamber 82 of the third cylinder body 74.

Also in the fourth embodiment, the thickness of the intermediate shaft portion 89 along the axial direction of the rotating shaft 78 and the length of the bearing hole 98 of the second intermediate partition plate 76 can be sufficiently secured. Therefore, as in the third embodiment, it is possible to prevent the oil film of the lubricating oil separating between the outer peripheral surface of the intermediate shaft portion 89 and the inner peripheral surface of the bearing hole 98 from being interrupted, and the intermediate shaft portion 89 of the rotating shaft 78. The lubricity can be improved.

Further, even when the compression mechanism portion 71 is assembled, the second intermediate partition plate 76 is moved from the second journal portion 87b side of the rotary shaft 78 to the intermediate shaft portion by the amount that the second intermediate partition plate 76 is thinned. It can be easily moved toward 89. Therefore, workability at the time of assembling the compression mechanism portion 71 is improved.

In the above embodiment, a twin rotary compressor having two rollers and a triple rotary compressor having three rollers have been described, but the present invention can be similarly applied to, for example, a rotary compressor having four or more cylinder bodies.

Furthermore, the rotary compressor is not limited to a vertical rotary compressor in which the rotary shaft is placed vertically, but may be a horizontal rotary compressor in which the rotary shaft is placed horizontally.

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, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 2,70 ... Rotary compressor, 4 ... Outdoor heat exchanger, 5 ... Expansion apparatus, 6 ... Indoor heat exchanger, 7 ... Circulation circuit, 10 ... Sealed container, 11 ... Electric motor, 12, 71 ... Compression mechanism part, 16, 17, 72, 73, 74 ... cylinder bodies (first cylinder body, second cylinder body, third cylinder body), 18, 60, 76 ... intermediate partition plate (second intermediate partition plate), 20 ... First bearing, 21... Second bearing, 22, 78... Rotating shaft, 24, 30, 80, 81, 82... Cylinder chamber (first cylinder chamber, second cylinder chamber, third cylinder chamber) 40a, 87a ... first journal part, 40b, 87b ... second journal part, 41a, 41b, 88a, 88b, 88c ... crank part (first crank part, second crank part, third crank Part), 52, 98 ... bearing hole , I: Lubricating oil.

Claims (12)

1. A cylindrical sealed container;
   A compression mechanism for compressing the refrigerant inside the sealed container;
   An electric motor housed in the sealed container and driving the compression mechanism,
   A rotary compressor in which the compression mechanism is lubricated with lubricating oil stored in the sealed container;
   The compression mechanism is
   A first bearing and a second bearing arranged at intervals in the axial direction of the sealed container;
   A plurality of cylinder bodies arranged between the first bearing and the second bearing and arranged in the axial direction of the hermetic container at intervals, each defining a cylinder chamber;
   An intermediate partition plate interposed between the cylinder bodies adjacent to each other and having a bearing portion;
   Positioned between the first journal part supported by the first bearing, the second journal part supported by the second bearing, and between the first journal part and the second journal part. And a rotating shaft having a plurality of crank portions that rotate eccentrically in the cylinder chamber, and an intermediate shaft portion slidably supported by the bearing portion of the intermediate partition plate between the adjacent crank portions, Including
   The intermediate shaft portion of the rotating shaft is provided at a position offset toward one of the crank portions between the adjacent crank portions, and the intermediate partition between the other crank portion and the intermediate shaft portion. A rotary compressor provided with a gap larger than the thickness of the bearing portion of the plate.
2. 2. The rotary compressor according to claim 1, wherein a gap along the axial direction of the rotating shaft is provided between the one crank portion and the intermediate shaft portion.
3. The rotary compressor according to claim 1, further comprising a spacer interposed between the intermediate partition plate and the cylinder body corresponding to the other crank portion, and the rotating shaft passes through the spacer.
4. The rotary compressor according to claim 1, wherein the rotating shaft is an integral structure in which the first journal portion, the second journal portion, the plurality of crank portions, and the intermediate shaft portion are integrally formed.
5. The rotary compressor according to claim 4, wherein the bearing portion of the intermediate partition plate has a bearing hole into which the other crank portion can be inserted.
6. The rotary compressor according to claim 4, wherein the diameter of the intermediate shaft portion is equal to or larger than the diameter of the other crank portion.
7. The rotary compressor according to claim 4, wherein the diameter of the other crank portion is smaller than the diameter of the one crank portion.
8. The suction port to which a suction pipe connected to an accumulator is connected and two branch passages branched from the suction port toward the adjacent cylinder chamber are formed inside the intermediate partition plate. The rotary compressor according to claim 3.
9. The rotary compressor according to claim 1 or 8, wherein the intermediate partition plate has a relief recess continuous to the bearing portion, and the relief recess has a shape larger than the diameter of the other crank portion.
10. The intermediate partition plate has an end face facing the cylinder body corresponding to the other crank part, and one end of the branch path and the escape recess are opened side by side on the end face. 10. The rotary compressor according to claim 9, wherein the escape recess is opened on the end face of the intermediate partition plate at a position deviated in a direction away from the opening end of the branch passage with respect to a central axis of the rotating shaft.
11. The spacer has an end surface that is exposed to the crank chamber corresponding to the other crank portion and in which a roller fitted to the outer peripheral surface of the other crank portion is slidably in contact with the intermediate portion. 11. The rotary according to claim 10, wherein a communication port that communicates the one branch passage of the partition plate with the other cylinder chamber, and a through hole through which the rotating shaft passes and continues to the escape recess are opened. compressor.
12. As the refrigerant circulates, a circulation circuit to which a radiator, an expansion device and a heat absorber are connected;
    The rotary compressor according to claim 1, connected to the circulation circuit between the radiator and the heat absorber.
    A refrigeration cycle apparatus comprising:

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