WO2011102413A1

WO2011102413A1 - Rotary compressor and refrigeration cycle device

Info

Publication number: WO2011102413A1
Application number: PCT/JP2011/053372
Authority: WO
Inventors: 康治里舘; 俊公青木; 和高島
Original assignee: 東芝キヤリア株式会社
Priority date: 2010-02-18
Filing date: 2011-02-17
Publication date: 2011-08-25
Also published as: CN102762868A; JPWO2011102413A1; CN102762868B; JP5358018B2

Abstract

Provided are a rotary compressor and a refrigeration cycle device equipped with the rotary compressor. The rotary compressor is equipped with: a primary bearing and a secondary bearing which are arranged above and below a cylinder; and an end bearing which is located at the motor section-side end of the rotating shaft, and the rotary compressor is configured so that the rotational balance when the rotating shaft rotates is maintained. A solid lubricating agent is applied to the sliding surfaces between the rotating shaft and primary and secondary bearings. The gap between the rotating shaft and the primary and secondary bearings when the solid lubricating agent is applied is set to be less than the gap between the rotating shaft and the end bearing, and the gap between the rotating shaft and the primary and secondary bearings when the solid lubricating agent is not applied is set to be greater than the gap between the rotating shaft and the end bearing.

Description

Rotary compressor and refrigeration cycle apparatus

The present invention relates to a rotary compressor and a refrigeration cycle apparatus using the same, and more particularly to a rotary compressor having an improved bearing support structure and a refrigeration cycle apparatus using the same.

Generally, a hermetic rotary compressor is provided with an electric motor part, a compression mechanism part, and a rotary shaft for transmitting rotational power generated in the motor part to the compression mechanism part in the hermetic case. It is rotatably supported by a main bearing and a sub-bearing provided to sandwich the cylinder of the compression mechanism section.

In order to reduce the size of the rotary compressor, it is conceivable to reduce the inner diameter of the cylinder of the compression mechanism and reduce the diameter of the rotary shaft. However, in this case, if the rotating shaft is supported only by the main bearing and the sub-bearing of the compression mechanism section, deflection occurs on the motor section side of the rotating shaft, and it is difficult to maintain the rotation balance of the motor. This may cause vibration and noise, and may impair reliability. In order to solve this problem, conventionally, in addition to the main bearing and the sub-bearing, a third bearing is provided as an end bearing at the end of the rotating shaft on the motor portion side, and the rotation balance when the rotating shaft rotates is maintained. A rotary compressor has been proposed. (Patent Document 1)
However, a clearance is required between the rotary shaft and the main and sub-bearings to maintain the lubrication of the sliding surface during the rotational movement. In addition, it is necessary to perform alignment to maintain a constant gap between the main and sub-bearings and the rotating shaft, and to align the shaft centers of the main and sub-bearings and the end bearings. There is.

If the accuracy in this alignment process is low, the sliding surface of the rotating shaft, the main bearing, and the sub-bearing may cause wear of the sliding surface due to falling off of the lubricating film, poor contact, noise, and reduced reliability.

Also, in order to perform this alignment process, it is necessary to make an initial investment for manufacturing equipment and increase the number of processes at the time of manufacturing, which increases the manufacturing cost.

JP 2001-323866 A

SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary compressor that can easily perform the alignment process when assembling the end bearing, is easy to manufacture, and has high reliability during operation, and a refrigeration equipped with the rotary compressor. To provide a cycle device.

One embodiment for solving the above-described problems of the present invention is that a sealed case includes a rotating shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion, a rotor fixed to the rotating shaft, and the sealed case. A motor portion having a stator fixed to a wall surface, a main bearing that slides with the main shaft portion, a compression mechanism portion that has a sub-bearing that slides with the sub shaft portion, and an end portion of the rotating shaft on the motor side In a rotary compressor provided with an end bearing that supports the shaft end portion positioned,
A solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing,
In the state of the base material in which the solid lubricant is not applied to each sliding surface, the gap between the main bearing portion and the main bearing is d1, the gap between the auxiliary bearing and the auxiliary bearing portion is d2, and the end bearing. When the gap between the shaft end of the rotating shaft and d3 is d3,
d1> d3
d2> d3
In relation to
When the solid lubricant is applied, the gap between the main bearing and the main bearing is d1 ′, and the gap between the sub-bearing and the sub-bearing is d2 ′.
d1 ′ <d3
d2 ′ <d3
It was.

In another embodiment of the present invention, a rotating shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion, a rotor fixed to the rotating shaft, and a wall surface of the sealed case are fixed in a sealed case. A motor portion having a stator, a main bearing that slides with the main shaft portion, a compression mechanism portion that has a sub-bearing that slides with the sub shaft portion, and the shaft end that is located at an end of the rotating shaft on the motor side In a rotary compressor comprising an end bearing that supports the part,
The end bearing is a rolling bearing;
A solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing,
In the state of the base material to which the solid lubricant is not applied, the gap between the main bearing and the main shaft portion is d1, the gap between the sub bearing and the sub bearing is d2, and the shaft end portions of the end bearing and the rotary shaft When the sum of the gap and the internal clearance is d4,
d1> d4
d2> d4
In relation to
In the state where the solid lubricant is applied, when the gap between the main bearing and the main shaft portion is d1 ′, and the gap between the sub bearing and the sub shaft portion is d2 ′,
d1 ′ <d4
d2 ′ <d4
It was.

Furthermore, a refrigeration cycle apparatus according to an embodiment of the present invention includes the above rotary compressor, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger, which are sequentially connected by piping. A refrigeration cycle is configured.

According to the embodiment of the present invention having the above-described features, a rotary compressor that can easily perform the alignment process when assembling the end bearing, is easy to manufacture, and has high reliability during operation is provided. In addition, it is possible to provide a refrigeration cycle apparatus including a rotary compressor having such characteristics.

The conceptual diagram of the refrigerating-cycle apparatus carrying the rotary compressor which concerns on embodiment of this invention. The longitudinal cross-sectional view of one Embodiment of the rotary compressor which concerns on the 1st Embodiment of this invention. The conceptual diagram which shows the clearance gap between the rotating shaft and each bearing of the rotary compressor which concerns on the 1st Embodiment of this invention. The conceptual diagram which shows the state of the rotating shaft and each bearing which were inclined of the rotary compressor which concerns on embodiment of this invention. The conceptual diagram which shows the state of the inclined rotating shaft and each bearing which are not made | formed of solid lubrication of a rotary compressor. The longitudinal cross-sectional view which shows the bearing member of the edge part bearing of the rotary compressor which concerns on the 2nd Embodiment of this invention. The conceptual diagram which shows the clearance gap between the rotating shaft and each bearing of the rotary compressor which concerns on the 2nd Embodiment of this invention.

A sealed rotary compressor according to an embodiment of the present invention and a refrigeration cycle apparatus using the rotary compressor will be described with reference to the accompanying drawings. In addition, in the following description, the description which shows an up-down, left-right, equal direction is a description in the state of illustration or an actual attachment state.

FIG. 1 shows an outline of the refrigeration cycle apparatus of the present invention. The refrigeration cycle apparatus of the present invention is used in, for example, an air conditioner, and includes a hermetic rotary compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion device 4, and an indoor heat exchanger 5, which are sequentially piped. The refrigeration cycle is configured by connecting with.

During cooling, the refrigerant discharged from the rotary compressor 1 is supplied to the outdoor heat exchanger 3 through the four-way valve 2 as indicated by solid arrows, and is condensed by exchanging heat with the outside air. The condensed refrigerant flows out of the outdoor heat exchanger 3 and flows to the indoor heat exchanger 5 through the expansion device 4, where it evaporates by exchanging heat with the indoor air and cools the indoor air. The refrigerant that has flowed out of the indoor heat exchanger 5 is sucked into the hermetic compressor 1 through the four-way valve 2.

Further, at the time of heating, the refrigerant discharged from the rotary compressor 1 is supplied to the indoor heat exchanger 3 through the four-way valve 2 as indicated by broken arrows, where it is condensed by exchanging heat with indoor air, Heat the room air. The condensed refrigerant flows out of the indoor heat exchanger 5 and flows to the outdoor heat exchanger 3 through the expansion device 4, where it evaporates by exchanging heat with outdoor air.

The evaporated refrigerant flows out of the outdoor heat exchanger 3 and is sucked into the hermetic compressor 1 through the four-way valve 2. Thereafter, the refrigerant is sequentially flown in the same manner, and the operation of the refrigeration cycle is continued.

This refrigeration cycle apparatus uses a chlorofluorocarbon refrigerant such as HFC or a natural refrigerant such as CO ₂ as a working fluid.

Also, this refrigeration cycle apparatus can be used for a heat pump water heater or a chilling unit.

FIG. 2 shows a longitudinal sectional view of the rotary compressor 1. The rotary compressor 1 includes an electric motor part 12 in the upper part of the sealed case 11 and a compressor part 13 in the lower part. The electric motor part 12 and the compressor part 13 are connected by a rotating shaft 14 for transmitting power. Yes.

More specifically, the electric motor unit 12 includes a stator 31 fixed to the inner wall surface of the sealed case 11 and a rotor 32 fixed to the rotating shaft, and the stator 31 supplies input power through a connection line 25a. For this purpose, it is connected to a sealing terminal 25 for the purpose.

The compression mechanism unit 13 includes a first compression mechanism unit 13A and a second compression mechanism unit 13B. The first compression mechanism unit 13A is disposed on the upper side and includes a first cylinder 41A. . The second compression mechanism portion 13B is disposed at a lower portion with respect to the first cylinder 41A via an intermediate partition plate 43, and includes a second cylinder 41B.

The first and

second cylinders

41A and 41B have the same inner diameter. A main bearing 15 as a first bearing is superposed on an upper surface portion of the first cylinder 41A, and is fixed to the first cylinder 41A by a mounting bolt 17a together with a discharge muffler 16a.

The secondary bearing 18 as a second bearing is overlaid on the lower surface of the second cylinder 41B, and is fixed to the second cylinder 41B with a mounting bolt (not shown) together with the discharge muffler 16b. The integrated second cylinder 41B, auxiliary bearing 18 and discharge muffler 16b are fixedly attached to the first cylinder 41A by mounting bolts 17b, and the compression mechanism 13 is assembled. In the assembled compression mechanism 13, the first cylinder 41A is fixed to the sealed case 11 by, for example, arc spot welding.

The lower end of the rotary shaft 14 is rotatably supported by the auxiliary bearing 18, and the upper portion thereof is rotatably supported by the main bearing 15. Further, the rotating shaft 14 penetrates through the first and

second cylinders

41A and 41B, and integrally includes two

eccentric portions

19a and 19b formed with a 180 ° phase difference.

The

eccentric portions

19a and 19b have the same diameter, and are assembled so as to be positioned at the inner diameter portions of the first and

second cylinders

41A and 41B. The

rollers

45a and 45b having the same diameter are fitted on the peripheral surfaces of the

eccentric portions

19a and 19b. The lengths in the axial direction of the

rollers

45a and 45b are substantially the same as the plate thicknesses (axial lengths) of the first cylinder 41A and the second cylinder 41B.

The first cylinder 41A and the second cylinder 41B are divided into upper and lower surfaces by the main bearing 15, the intermediate partition plate 43, and the auxiliary bearing 18, and the

rollers

45a and 45b are accommodated in the respective interiors so as to be eccentrically rotatable. One cylinder chamber 42a and a second cylinder chamber 42b are formed. Each

roller

45a, 45b can rotate eccentrically in the first and second cylinder chambers 42a, 42b.

The first and

second cylinders

41A and 41B are provided with

blade grooves

46a and 46b, and the

blade grooves

46a and 46b are open to the cylinder chambers 42a and 42b.

Blades

47a and 47b and

spring members

48a and 48b are accommodated in the

blade grooves

46a and 46b, respectively.

Each

blade

47a, 47b is formed in a substantially semicircular shape in a plan view at the tip portion on the side of each cylinder chamber 42a, 42b. The

spring members

48a and 48b are interposed between the rear ends of the

blades

47a and 47b and the end surfaces of the

blade grooves

46a and 46b. The

spring members

48a and 48b apply elastic force (back pressure) to the

blades

47a and 47b, and the tip ends of the cylinder chambers 42a and 42b. And elastically contact the peripheral surfaces of the

rollers

45a and 45b.

Accordingly, when the rotating shaft 14 rotates, the

eccentric portions

19a and 19b rotate eccentrically, and the

rollers

45a and 45b rotate eccentrically (turn) along the inner peripheral walls of the cylinder chambers 42a and 42b, the

blades

47a and 47b It reciprocates along the

blade grooves

46a and 46b and makes linear contact with the

rollers

45a and 45b regardless of the rotation angle of the

rollers

45a and 45b, thereby partitioning each cylinder chamber 42a and 42b into a suction chamber and a compression chamber (not shown). It becomes. The suction chamber is connected to the accumulator 105 through

suction pipes

26a and 26b.

The

blades

47a and 47b are formed in such a length dimension that the rear ends are located in the

blade grooves

46a and 46b when the tips are at the most protruding portions into the cylinder chambers 42a and 42b. When the

blades

47a and 47b are most retracted, the distance between the rear ends of the

blades

47a and 47b and the end surfaces of the

blade grooves

46a and 46b is formed to be slightly larger than the maximum compression length of the

spring members

48a and 48b.

The main bearing 15 and the sub-bearing 18 are provided with a discharge valve mechanism (not shown), which respectively communicates with the cylinder chambers 42a and 42b and is covered with

discharge mufflers

16a and 16b.

As will be described later, the discharge valve mechanism is opened with the refrigerant gas compressed in each cylinder chamber 42a, 42b rising to a predetermined pressure, and the refrigerant gas is discharged from each cylinder chamber 42a, 42b into the

discharge mufflers

16a, 16b. It is supposed to be.

Further, a refrigerating machine oil 50 as a liquid lubricant is stored below the inside of the sealed case 11 and is sucked up by a rotary pump (not shown) penetrating the center of the rotary shaft 14 to lubricate each sliding portion.

A bearing member 20 is provided between one end of the sealed case 11 and the electric motor unit 3, and the bearing member 20 includes an end bearing 21 that is a third bearing that pivotally supports the rotating shaft 14, and this end. It comprises a bearing frame portion 22 that holds the partial bearing 21.

The end bearing 21 is, for example, a sliding bearing or a rolling bearing. In the present embodiment, it is a sliding bearing, and supports the vicinity of the upper end of the rotating shaft 14.

The bearing frame portion 22 is provided with a disk-shaped main portion 22a. A flange portion 22b for press-fitting is provided on the outer periphery of the main portion 22a. The end bearing 21 is a bearing provided at the center of the bearing frame portion 22. It is attached to the attachment hole 22c and is fixed by a bolt (not shown).

Further, an oil separation member 23 is screwed onto the upper end of the rotating shaft 14 above the bearing frame portion 22.

Therefore, as described above, the refrigerant gas that has flowed out to the upper side of the electric motor unit 12 passes through a gas hole (not shown) provided in the bearing frame 22, and the oil contained in the refrigerant gas is separated by the oil separation member 23, and is sealed. It is discharged out of the sealed case 11 through a discharge pipe 24 provided on the upper part of the case 11.

As shown in FIG. 3, a surface treatment with a solid lubricant 35 is performed between the rotary shaft 14 and the main bearing 15 and the sub-bearing 18. For example, the main shaft portion 36 that is a sliding surface with the main bearing 15 of the rotating shaft 14 and the subshaft portion 37 that is a sliding surface with the sub bearing 18 of the rotating shaft 14 are phosphoric acid that is a solid lubricant over the entire circumference. A salt film is applied.

A main shaft gap and a sub shaft gap are provided as clearances for sliding between the rotary shaft 14 and the main bearing 15 and the sub bearing 18, and the main shaft gap between the base materials not including the solid lubricant 35 is provided. And the average of the sub-shaft gap are d1 and d2, respectively, and the width of the main shaft gap and the sub-shaft gap including the solid lubricant 35 are d1 ′ and d2 ′, respectively.

Further, if the average of the gaps between the end bearing 21 located at the upper part of the electric motor unit 12 and the rotary shaft 14 is d3, the gaps have a relationship of d1> d3, d2> d3, d1 ′ <d3, d2 ′ <d3. Set to be.

With such a configuration, the gap between the rotary shaft 14, the main bearing 15 and the auxiliary bearing 18 can be initially narrowed by the solid lubricant 35 during assembly. That is, as shown in FIGS. 4 and 5, the relationship between the maximum inclination angle θ1 when the solid lubricant is applied and assembled and the maximum inclination angle θ2 when only the base material is assembled is θ1 <θ2. . Even when the rotary shaft 14 is tilted before the end bearing 21 is assembled, the solid lubricant 35 contacts the inner peripheral surface of the bearing, and the maximum tilt angle of the rotary shaft 14 is made smaller than that of the base material alone. can do. Therefore, when the end bearing 21 is assembled, the center of the end bearing 21 and the main bearing 15 and the sub-bearing 18 are misaligned with simple alignment without performing alignment using dedicated equipment. Integration is possible in the minimum state.

Further, in the contact portions A and B between the inclined rotating shaft 14 and the main bearing 15 and the sub-bearing 18, even if the solid lubricant 35 falls off due to long-time operation of the compressor, the base materials do not contact each other. A gap necessary for lubrication with the refrigerating machine oil can be secured.

Further, when the main bearing 15 is longer in the rotation axis direction of the main bearing 15 and the sub-bearing 18, the relation of d1> d2 and d1 ′> d2 ′ is further established, and when the sub-bearing 18 is longer. If the relations of d1 <d2 and d1 ′ <d2 ′ are satisfied and the lengths of the main bearing 15 and the auxiliary bearing 18 are the same, d1 = d2 and d1 ′ = d2 ′.

This is because, if the axial length of each bearing is large when the rotating shaft 14 is inclined, the amount of eccentricity of the rotating shaft 14 with respect to the center axis of each bearing becomes large, so that the width of the gap to be secured is allowed. This is because an appropriate bearing length is set according to the inclination angle.

In the present embodiment, since the axial length of the main bearing 15 is longer than the auxiliary bearing 18, d1> d2 is d1 ′> d2 ′.

A rotary compressor according to a second embodiment of the present invention will be described with reference to FIGS.

In the rotary compressor according to the second embodiment, the end bearing 21 is a rolling bearing, in particular, a ball bearing 28 having an automatic alignment mechanism, and supports the vicinity of one end of the rotating shaft 14, for example, the vicinity of the upper end. explain.

The compressor in the second embodiment is incorporated into the refrigeration cycle apparatus in the same manner as the rotary compressor 1 in the first embodiment, and the configuration thereof is the same as that of the rotary compressor in the first embodiment. The configuration is almost the same (FIG. 2), and the configurations of the end bearing 21 and the bearing member 20 are different as shown in FIG.

As shown in FIG. 6, the bearing frame portion 51 is provided with a disk-shaped main portion 51a, and a flange portion 51b for press-fitting is provided on the outer periphery of the main portion 51a. It is attached to a bearing attachment hole 51d provided in the boss portion 51c of 51.

Further, as shown in FIG. 7, the average of the main shaft gap and the average of the sub shaft gap between the base materials not including the solid lubricant 35 are d1 and d2, respectively. The average shaft clearance is defined as d1 ′ and d2 ′, respectively. When the average of the gaps between the ball bearing 28 and the rotary shaft 14 is d4, the relations between the gaps d1, d2, d1 ′, d2 ′, d4 are d1> d4, d2> d4, d1 ′ <d4, d2 ′ < d4.

Here, the average d4 of the gap between the ball bearing 28 and the rotary shaft 14 is a value including the average of the internal gap which is the gap between the inner ring 28a, the outer ring 28b and the ball 28c of the ball bearing 28. In the embodiment, a phosphate film is used as the solid lubricant 35, but in addition to this, a fluorine-based resin such as molybdenum disulfide and PTFE (polytetrafluoroethylene), or a solid lubricant such as graphite may be used.

Further, in the first and second embodiments, the example in which the solid lubricant is applied to the outer peripheral surfaces of the main shaft portion 36 and the sub shaft portion 37 of the rotating shaft 14 is shown. You may apply | coat to a surrounding surface. Also, the outer peripheral surface of the main shaft portion and the inner peripheral surface of the sub-bearing can be applied with a solid lubricant, and conversely, the outer peripheral surface of the sub-shaft portion and the inner peripheral surface of the main bearing can be applied with a solid lubricant. good. Further, a solid lubricant may be applied to both sliding surfaces on the rotating shaft side and the bearing side.

In the first and second embodiments, the surface to which the solid lubricant is applied is the entire circumference of the rotating shaft and the sliding surface of the bearing. However, in order to reduce the contact area between the rotating shaft and each bearing, it is partially It may be applied.

In the first and second embodiments, a two-cylinder rotary compressor is used, but a one-cylinder rotary compressor may be used.

In addition, as described first, the embodiment of the present invention provides a refrigeration cycle apparatus including the rotary compressor according to the above-described embodiment of the present invention.

That is, as shown in FIG. 1, the refrigeration cycle apparatus according to the present embodiment includes a hermetic rotary compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion device 4, and an indoor heat exchanger 5 in the above-described embodiment. The refrigeration cycle is configured by sequentially connecting them with piping.

During cooling, the refrigerant discharged from the rotary compressor 1 is supplied to the outdoor heat exchanger 3 through the four-way valve 2 as indicated by solid arrows, where it is condensed by exchanging heat with the outside air. The condensed refrigerant flows out of the outdoor heat exchanger 3 and flows to the indoor heat exchanger 5 through the expansion device 4, where it evaporates by exchanging heat with the indoor air and cools the indoor air. The refrigerant that has flowed out of the indoor heat exchanger 5 is sucked into the hermetic compressor 1 through the four-way valve 2.

Also, this refrigeration cycle device can be used for heat pump water heaters, chilling units, and the like.

The present invention is not limited to the embodiments described above, and may include various changes and modifications without departing from the spirit described in the claims.

DESCRIPTION OF SYMBOLS 1 ... Rotary compressor, 2 ... Four-way valve, 3 ... Outdoor heat exchanger, 4 ... Expansion device, 5 ... Indoor heat exchanger, 11 ... Sealed case, 12 ... Electric motor part, 13 ... Compressor part, 14 ... Rotating shaft 15 ... Main bearing, 16A ... Discharge muffler, 16B ... Discharge muffler, 17a ... Mounting bolt, 17b ... Mounting bolt, 18 ... Sub-bearing, 19a ... Eccentric part, 19b ... Eccentric part, 20 ... Bearing member, 21 ... End Bearing, 22 ... Bearing frame, 22a ... Main part, 22b ... Flange, 22c ... Bearing mounting hole, 23 ... Oil separation member, 24 ... Discharge pipe, 25 ... Sealed terminal, 26 ... Suction pipe, 28 ... Ball bearing, 31 ... Stator, 32 ... Rotor, 33 ... Motor gap, 35 ... Solid lubricant, 36 ... Main shaft part, 37 ... Sub shaft part, 38 ... Main shaft gap, 39 ... Sub shaft gap, 41A ... Cylinder, 41B ... Cylinder, 42a ... cylinder chamber, 42b ... cylinder chamber, 43 ... intermediate partition plate, 45a ... roller, 45b ... roller, 46a ... blade groove, 46b ... blade groove, 47a ... blade, 47b ... Blade, 48a ... Spring member, 48b ... Spring member, 50 ... Refrigerating machine oil, 51 ... Bearing frame, 51a ... Main part, 51b ... Flange part, 51c ... Boss part, 51d ... Bearing mounting hole, 105 ... Accumulator

Claims

A rotary shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion in a sealed case, a motor portion having a rotor fixed to the rotary shaft, and a stator fixed to the wall surface of the sealed case, and the main shaft portion And a compression mechanism having a secondary bearing that slides with the secondary shaft, and an end bearing that supports the shaft end located at the motor-side end of the rotating shaft. In rotary compressor,
A solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing,
In the state of the base material in which the solid lubricant is not applied to each sliding surface, the gap between the main bearing portion and the main bearing is d1, the gap between the auxiliary bearing and the auxiliary bearing portion is d2, and the end bearing. When the gap between the shaft end of the rotating shaft and d3 is d3,
d1> d3
d2> d3
In relation to
When the solid lubricant is applied, the gap between the main bearing and the main bearing is d1 ′, and the gap between the sub-bearing and the sub-bearing is d2 ′.
d1 ′ <d3
d2 ′ <d3
A rotary compressor characterized by the following relationship.
2. The rotary compressor according to claim 1, wherein the solid lubricant is at least one of a phosphate coating, molybdenum disulfide, a fluorine-based resin, and graphite.
A rotary shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion in a sealed case, a motor portion having a rotor fixed to the rotary shaft, and a stator fixed to the wall surface of the sealed case, and the main shaft portion And a compression mechanism having a secondary bearing that slides with the secondary shaft, and an end bearing that supports the shaft end located at the motor-side end of the rotating shaft. In rotary compressor,
The end bearing is a rolling bearing;
A solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing,
In the state of the base material to which the solid lubricant is not applied, the gap between the main bearing and the main shaft portion is d1, the gap between the sub bearing and the sub bearing is d2, and the shaft end portions of the end bearing and the rotary shaft And the sum of the internal clearances of the end bearings and d4,
d1> d4
d2> d4
In relation to
In the state where the solid lubricant is applied, when the gap between the main bearing and the main shaft portion is d1 ′, and the gap between the sub bearing and the sub shaft portion is d2 ′,
d1 ′ <d4
d2 ′ <d4
A rotary compressor characterized by the following relationship.
The rotary compressor according to claim 3, wherein the rolling bearing includes an automatic alignment mechanism.
4. The rotary compressor according to claim 3, wherein the solid lubricant is at least one of a phosphate film, molybdenum disulfide, a fluorine-based resin, and graphite.
The rotary compressor according to claim 1, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger are provided, and a refrigeration cycle is configured by sequentially connecting them through piping. A refrigeration cycle device.
The rotary compressor according to claim 3, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger are provided, and a refrigeration cycle is configured by sequentially connecting them through piping. A refrigeration cycle device.