JP5360711B2 - Hermetic rotary compressor and refrigeration cycle equipment - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hermetic rotary compressor improving reliability by regulating the maximum deformation amount of a roller on which a concentration load is applied and ensuring smooth rotations, and a refrigerating cycle device equipped with the hermetic rotary compressor and capable of improving a refrigerating efficiency. <P>SOLUTION: The hermetic rotary compressor 1 fits an inner ring portion 23a of a rolling bearing 23 with a rotating shaft eccentric portion 13a, and an outer ring portion 23b is also used as a roller. A track surface M of a rolling element 23c interposed between the inner ring portion and the outer ring portion is formed on a roller inner diameter portion. If assuming that the width dimensions of a blade 27 is T[mm], an outer diameter portion radius of the roller is Rr[mm], the outermost peripheral radius of a roller inner diameter portion track surface M is Ri[mm], the Young's modulus of the roller is Er[MPa], a distance on a track ring between the rolling elements is C[mm], and differential pressure between discharging pressure and sucking pressure is &Delta;P[MPa], the expression (1):0.001[mm]&ge;T*&Delta;P/16Er*(C/(Rr-Ri))<SP>3</SP>is satisfied. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a hermetic rotary compressor in which a rolling bearing is fitted to an eccentric part of a rotating shaft and the outer ring part of the rolling bearing is also used as a roller with which a blade contacts, and the hermetic rotary compressor is used as a refrigeration cycle. The present invention relates to a refrigeration cycle apparatus provided as a component.

  A hermetic rotary compressor that has been frequently used conventionally includes an electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft in a hermetic case. The compression mechanism includes a cylinder that forms a cylinder chamber, a roller that fits in an eccentric portion provided on the rotating shaft, and a blade that receives a back pressure by a compression spring and a tip edge of which contacts a roller outer peripheral surface. Yes.

  Due to such a structure, the compression operation itself is smoothly performed without any trouble. However, the roller interposed between the rotating shaft eccentric part and the blade functions as a slide bearing. The inner diameter of the roller is larger than the diameter of the rotating shaft, and the large diameter portion rotates, resulting in a large friction loss as a slide bearing, which hinders improvement in efficiency.

  As a part of the development of a new technology that seeks a smoother compression action and improves compression efficiency, the present inventors have focused on a roller that is fitted to the eccentric part of the rotating shaft and the tip edge of the blade contacts. [Patent Document 1] has been disclosed. In this new technology, rolling bearings are provided in at least one of the rotating shaft, the main bearing, the auxiliary bearing, and the roller to improve the oil supply efficiency.

  Specifically, the rolling bearing is attached to the eccentric portion of the rotating shaft, the blade tip edge is brought into contact with the outer peripheral surface of the outer ring portion, and the outer ring portion is also used as a roller. That is, a roller bearing is provided as a roller, friction loss can be reduced, and compression efficiency can be improved.

JP 2007-291996 A

  By the way, the rolling bearing is generally interposed between the fixed body and the rotating body, so that no concentrated load is applied. For example, in a rolling bearing used between an axle and a wheel, not only an inner ring part fitted into the axle but also an outer ring part fitted into the wheel can be partially applied with no concentrated load.

  Therefore, it is not necessary to consider the maximum deformation amount (deflection amount) of the outer ring portion and the inner ring portion in the rolling bearing in the range normally used. On the other hand, as described above, when the compression mechanism portion of the hermetic rotary compressor is also used as the outer ring portion of the rolling bearing as a substitute for the roller, the tip edge of the blade subjected to the back pressure presses the roller, It is inevitable that a concentrated load is applied to the roller.

Under operating conditions where the differential pressure between the suction pressure and the discharge pressure is large, the raceway surface of the rolling element (ball) formed on the inner diameter portion of the roller may be deformed due to the concentrated load. As a result, flaking (metal peeling of the raceway surface) occurs and the reliability of the rolling bearing is impaired.
In the above-mentioned [Patent Document 1], no measures against the above-mentioned anxiety factor have been taken into consideration.

  The present invention has been made on the basis of the above circumstances. The purpose of the present invention is to apply a concentrated load from the blade by fitting a rolling bearing to the eccentric portion of the rotating shaft and also using the outer ring portion as a roller. The maximum amount of deformation of the roller caused by the above is suppressed to the minimum, and the rotary type compressor that can improve the reliability by ensuring smooth rotation, and the refrigeration efficiency is provided with the hermetic type rotary compressor. It is an object of the present invention to provide a refrigeration cycle apparatus that can improve.

In order to satisfy the above object, a hermetic rotary compressor according to the present invention accommodates an electric motor unit and a compression mechanism unit coupled to the electric motor unit via a rotating shaft in a hermetic case, and the compression mechanism unit. The cylinder in which the cylinder chamber is formed, a roller that fits in the eccentric part of the rotating shaft and makes an eccentric motion in the cylinder chamber, and is provided in a freely reciprocating manner in the cylinder so as to abut on the outer peripheral surface of the roller and bisect the cylinder chamber Blade, a discharge valve mechanism for guiding the high pressure gas compressed in the cylinder chamber into the sealed case, and a high pressure gas provided in the cylinder and discharged from the discharge valve mechanism into the sealed case to the blade rear end A back pressure applying means for applying back pressure to the
The rolling ring raceway surface interposed between the inner ring part and the outer ring part of the rolling bearing, in which the inner ring part of the rolling bearing is fitted to the rotating shaft eccentric part and the outer ring part of the rolling bearing is also used as a roller with which the blade contacts. Is formed on the inner diameter part of the roller which is the inner diameter part of the outer ring part,
The width of the blade is T [mm], the outer radius of the roller is Rr [mm], the outermost radius of the inner raceway surface of the roller is Ri [mm], the Young's modulus of the roller is Er [MPa], When the distance between the moving bodies on the raceway is C [mm] and the differential pressure between the discharge pressure and the suction pressure during the compressor operation is ΔP [MPa], the following relational expression (1) is established.

According to the hermetic rotary compressor of the present invention, on the premise that the outer ring portion of the rolling bearing is also used as a roller, the maximum deformation amount of the roller to which concentrated load is applied is restricted to the minimum to ensure smooth rotation. To improve reliability.
According to the refrigeration cycle apparatus of the present invention, the above-described hermetic rotary compressor is provided as a refrigeration cycle component, and an improvement in refrigeration cycle efficiency can be obtained.

The longitudinal cross-sectional view of the hermetic type rotary compressor based on embodiment in this invention, and the refrigeration cycle block diagram of a refrigeration cycle apparatus. The cross-sectional top view of the compression mechanism part in the sealed rotary compressor based on the embodiment. The cross-sectional top view of a part of compression mechanism part based on the embodiment. The figure which expanded a part of FIG. 3 based on the embodiment. The characteristic figure of the roller maximum deformation amount and fatigue life based on the embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a hermetic rotary compressor 1 and a refrigeration cycle configuration diagram of a refrigeration cycle apparatus R.
In the figure, reference numeral 1 denotes a hermetic rotary compressor (hereinafter simply referred to as “compressor”), which will be described later. A refrigerant pipe P is connected to the upper end portion of the compressor 1, and a condenser 2, an expansion valve (expansion device) 3, an evaporator 4 and an accumulator 5 are sequentially provided in the refrigerant pipe P. Further, the refrigerant pipe P is connected to the side of the compressor 1 from the accumulator 5, and these constitute the refrigeration cycle of the refrigeration cycle apparatus R.
Next, the compressor 1 will be described.
The compressor 1 includes a sealed case 10. The electric motor unit 11 is accommodated in the upper part of the sealed case 10, and the compression mechanism part 12 is accommodated in the lower part. The electric motor unit 11 and the compression mechanism unit 12 are integrally connected via a rotating shaft 13.

  An oil reservoir 14 for collecting lubricating oil is formed on the inner bottom of the sealed case 10, and most of the compression mechanism 12 disposed on the lower side is immersed in the lubricating oil. A refrigerant pipe P that is a discharge pipe communicating with the condenser 2 is connected to the upper surface portion of the sealed case 10, and a refrigerant pipe P that is a suction pipe communicating with the accumulator 5 is connected to the lower peripheral wall of the sealed case 10. The

  The motor unit 11 has a rotor (rotor) 15 fitted and fixed to the rotary shaft 13, and an inner peripheral surface thereof facing the outer peripheral surface of the rotor 15 with a narrow gap therebetween. It is comprised from the stator (stator) 16 inserted and fixed to.

Next, the compression mechanism 12 will be described with reference to FIGS.
FIG. 2 is an enlarged cross-sectional plan view showing the compression mechanism 12.
The compression mechanism unit 12 is fitted and fixed to the inner peripheral wall of the sealed case 10, and the cylinder 20 having an inner diameter hole in the shaft core, the main bearing 21 attached to the upper surface of the cylinder 20, and the auxiliary bearing 22 attached to the lower surface of the cylinder 20. It has. The cylinder inner diameter hole is a space that is closed by the main bearing 21 and the auxiliary bearing 22, and the space becomes a cylinder chamber S.

The rotary shaft 13 is rotatably supported by a portion between the motor unit 11 and the cylinder 20 upper surface that is penetrated by the main bearing 21. Further, the rotary shaft 13 is rotatably supported by the portion between the lower surface and the lower end of the cylinder 20 through the auxiliary bearing 22.
Both the main bearing 21 and the sub-bearing 22 are integrally projected along flange portions 21a and 22a that block the inner diameter hole of the cylinder 20 and the shaft core portions of the flange portions 21a and 22a. It consists of pivot parts 21b and 22b provided with bearing holes.

  The rotating shaft 13 is integrally provided with an eccentric portion 13a whose central axis is eccentric by a predetermined amount. A rolling bearing 23 described later is fitted to the peripheral surface of the eccentric portion 13a. The eccentric portion 13a and the rolling bearing 23 are accommodated in the cylinder chamber S, and a part of the outer peripheral surface of the rolling bearing 23 is designed to linearly contact the peripheral wall of the cylinder chamber S along the axial direction.

  The rolling bearing 23 is formed to have a predetermined thickness, and an inner ring portion 23a that is fitted in a loose state with an inner diameter portion of the rotary shaft eccentric portion 13a, and a part of the outer peripheral surface that is formed to have a predetermined thickness along the axial direction. The outer ring portion 23b that linearly contacts the circumferential wall of the cylinder chamber S and a plurality of rolling elements (balls) 23c interposed between the inner ring portion 23a and the outer ring portion 23b.

  If the rotating shaft 13 rotates, the contact position of the outer peripheral surface of the outer ring portion 23b with the peripheral wall of the cylinder chamber S gradually moves in the circumferential direction. That is, the outer ring portion 23b performs the same function as a conventionally used roller of a rotary compressor, and hence the outer ring portion 23b of the slide bearing 23 is hereinafter referred to as a “roller”.

  The cylinder 20 is provided with a blade chamber 25. The blade chamber 25 communicates a lateral hole 25a provided at a predetermined depth from the outer peripheral surface of the cylinder 20 in the axial direction, and a cylinder chamber S which is an inner diameter hole of the cylinder 20 and a distal end portion of the lateral hole 25a. And a blade receiving groove 25b provided over the upper and lower surfaces of the cylinder 20.

  A compression spring 26 is accommodated in the lateral hole 25a, and a blade 27 is accommodated in the blade accommodation groove 25b in a movable manner. One end of the compression spring 26 is in contact with the inner peripheral wall of the sealed case 10, and the other end is in contact with the rear end of the blade 27. The blade 27 receives a back pressure due to the elastic force of the compression spring 26, and the tip edge abuts the outer peripheral surface of the roller 23b along the axial direction to bisect the cylinder chamber S.

  A communication hole 28 is provided from the lower surface of the cylinder 20 to the horizontal hole 25 a, and the lubricating oil in the oil reservoir 14 is guided to the horizontal hole 25 a through the communication hole 28. The lubricating oil filling the lateral hole 25a applies back pressure to the rear end portion of the blade 27 and penetrates between both side surfaces of the blade 27 and both side walls of the blade accommodating groove 25b to ensure smooth movement of the blade 27. To do.

  Thus, the communication hole 28 together with the compression spring 26 constitutes a back pressure applying means J for the blade 27. However, it is the high-pressure lubricating oil led to the lateral hole 25 a through the communication hole 28 that substantially applies the back pressure to the blade 27. The compression spring 26 exists exclusively as auxiliary back pressure applying means J that performs a pressing action when the compression operation is started.

  On the other hand, the main bearing 21 is provided with a discharge hole 30. The position where the discharge hole 30 is provided is this one side portion in the vicinity of the portion where the leading edge of the blade 27 contacts the outer peripheral surface of the roller 23b. The discharge hole 30 is opened and closed by a discharge valve mechanism 31, and a valve cover 32 provided with a guide hole attached to the main bearing 21 and opening into the sealed case 10 covers the discharge valve mechanism 31.

  In the cylinder 20, a suction portion 33, which is a hole portion, is provided at a portion opposite to the discharge hole 30 across the contact portion of the blade 27 with the roller 23 b. The suction portion 33 is connected to a refrigerant pipe P that is a suction pipe that penetrates the cylinder 20 in the radial direction, communicates with the inside of the sealed case 10 and the cylinder chamber S, and communicates with the accumulator 5.

Next, the compression action of the hermetic rotary compressor 1 configured as described above and the refrigeration action of the refrigeration cycle apparatus R will be described.
By energizing the motor unit 11 constituting the compressor 1, the rotor 15 is rotated by the rotating magnetic field generated in the stator 16, and the rotating shaft 13 integrated with the rotor 15 is rotationally driven. A driving torque acts on the rotating shaft 13 from the electric motor unit 11, and the eccentric portion 13 a provided on the rotating shaft 13 and the rolling bearing 23 integrally perform an eccentric motion in the cylinder chamber S.

  A part of the cylinder chamber S becomes negative pressure, and the refrigerant is guided from the accumulator 5 through the refrigerant pipe P. The refrigerant is guided to a space part defined by the peripheral surface of the roller 23b, the peripheral surface of the cylinder chamber S, and the blade 27, and is compressed by reducing the capacity of the space part as the roller 23b rotates eccentrically.

When the space portion becomes the smallest, the refrigerant reaches a predetermined high pressure state and increases in temperature. The discharge valve mechanism 31 is opened by the high-temperature and high-pressure gas refrigerant, and is guided and filled into the sealed case 10 through the guide hole of the valve cover 32. The gas refrigerant filling the sealed case 10 is discharged to the refrigerant pipe P connected to the upper end portion of the sealed case 10.
The gas refrigerant exchanges heat with the outside air or water in the condenser 2 to be condensed and liquefied and converted into a liquid refrigerant. This liquid refrigerant is led to the expansion valve 3 and adiabatically expanded, and further led to the evaporator 4 to evaporate by exchanging heat with the air in the peripheral portion where the evaporator 4 is disposed.

  As the refrigerant evaporates, it takes away the latent heat of evaporation from the surrounding area and changes it to cool air. That is, it performs a freezing action on the peripheral part. The refrigerant evaporated in the evaporator 4 is guided to the accumulator 5 and separated into gas and liquid. Then, the refrigerant is sucked into the cylinder chamber S of the compressor 1 and compressed again to change into a high-temperature and high-pressure gas refrigerant, and the above-described refrigeration cycle is repeated.

Next, based on FIGS. 3 and 4, the roller 23b and the blade 27 constituting the compression mechanism 12 of the hermetic rotary compressor 1 will be described.
3 is an enlarged view of a part of the compression mechanism section 12, and FIG. 4 is an enlarged view of FIG.

  The blade 27 receives a back pressure by the elastic force of the compression spring 26 when the compression operation is started, and when the compression operation is stable, the high-pressure lubricating oil in the oil reservoir 14 passes from the communication hole 28 to the blade chamber 25. Back pressure is received by filling the horizontal hole 25a.

  The leading edge of the blade 27 receiving the back pressure contacts the roller 23b, and applies a concentrated load Fv [N] to the roller 23b. At this time, when the differential pressure between the suction pressure and the discharge pressure is large, the concentrated load Fv of the blade 27 on the roller 23b becomes excessive, or the rigidity of the roller 23b becomes small.

  For this reason, there is a possibility that the inner surface raceway surface M of the roller 23b with which the rolling element 23c comes into contact may be deformed, flaking or the like occurs, preventing smooth rotation of the roller 23b, and the reliability of the rolling bearing 23 is remarkably high. It will be damaged.

In order to provide this countermeasure, the maximum deformation amount σmax [mm] of the roller 23b in the load direction due to the concentrated load Fv of the blade 27 is obtained.
That is, the positions of the rolling elements 23c on both sides of the point of application of the concentrated load Fv from the blade 27 (contact point with the roller 23b) are set as fixed ends, and the roller 23b is approximated as a straight beam. Then, the following relational expression (2) is calculated | required from mechanical engineering handbook and A4 material dynamics.

The differential pressure between the discharge pressure and the suction pressure during operation of the compressor 1 is ΔP [MPa], the width of the blade 27 is T [mm], and the thickness of the blade 27 and the roller 23b (shown in FIG. 1) is H [mm]. The maximum value of the concentrated load Fv is obtained from the relational expression (3).
Fvmax [N] = ΔP · T · H (3)
Further, when the outer peripheral radius of the roller 23b is Rr [mm] and the outermost peripheral radius of the inner raceway surface M of the roller 23b is Ri [mm], the cross-sectional secondary moment Ir of the roller 23b is expressed by the relational expression (4). It is requested from.
^{Ir = H · (Rr-Ri} ) 3/12 ...... (4)
Substituting the above relational expressions (3) and (4) into the above relational expression (2) yields the following relational expression (5).

FIG. 5 is a characteristic diagram of the maximum deformation amount σmax of the roller 23b and the fatigue life ratio L / L0.
In this figure, when the maximum deformation amount σmax of the roller 23b in the load direction due to the concentrated load Fv of the blade 27 is 0, the rolling fatigue life on the inner raceway surface M of the roller 23b is L0, and the maximum deformation amount σmax of the roller 23b. Shows the relationship of rolling fatigue life to.
FIG. 5 shows that when the maximum deformation amount σmax of the roller 23b is 0.001 mm or more, the fatigue life is rapidly reduced.

  For example, in a normal usage method such as a rolling bearing used between an axle and a wheel, the raceway surface of the ball bearing (that is, the rolling element) follows the housing or the shaft. There is no fear of deformation. Therefore, it is not necessary to consider the maximum deformation amount σmax of the outer ring portion and the inner ring portion with respect to the rolling bearing in a normally used range.

On the other hand, as described above, when the outer ring portion 23b of the rolling bearing 23 is used as a substitute for the roller in the compression mechanism portion 12 in the hermetic rotary compressor 1, the concentrated load Fv due to the blade 27 receiving the back pressure is generated. It is inevitable that the roller 23b as the outer ring portion is applied.
When the rigidity of the roller 23b is low, deformation occurs in the raceway surface of the rolling element 23c, which is the inner diameter surface, and the rolling element 23c cannot be smoothly rolled. If the maximum deformation amount σmax of the roller 23b exceeds a certain value, flaking or the like occurs and the rolling life is rapidly reduced.

Therefore, from FIG. 5, by satisfying the following relational expression (1) where the maximum deformation amount σmax of the roller 23b is equal to or less than 0.001 mm, the rolling life is prevented from being lowered and the reliability is high. The compressor 1 can be obtained.

Furthermore, in the present invention, after satisfying the above relational expression (1), the following relation is obtained from the curvature radius Rv [mm] at the contact portion of the blade 27 with the roller 23b and the outer peripheral radius Rr [mm] of the roller 23b. With respect to the equivalent radius ρ [mm] calculated by Expression (7), the width dimension T [mm] of the blade 27 and the following relational expression (6) are established.
ρ ≧ T (6)
Here, 1 / ρ = 1 / Rv + 1 / Rr (7)
That is, the contact state between the roller 23b and the blade 27 can be replaced with a contact state of a cylindrical body having a different curvature, as shown in FIG.
Due to the concentrated load Fv of the blade 27 on the roller 23b, the roller 23b and the blade 27 come into surface contact. The elastic contact length d [mm] at that time is expressed by the relational expression (8) and can be developed into the relational expression (9).

A Hertz stress Pmax [MPa] expressed by the relational expression (10) is generated at the contact portion between the roller 23b and the blade 27. (Hertz's elastic contact theory)

When the Hertz stress Pmax is large, there is a high risk that abnormal wear will occur on the contact surface between the roller 23b and the blade 27, and the reliability decreases. Further, the rotation of the roller 23b is suppressed, and in the worst case, the roller 23b does not rotate. In this case, a load is always received at the same location on the inner raceway surface M of the roller 23b, and the life of the rolling bearing 23 is reduced.
With respect to this problem, the relational expression (10) is expressed by the following expression (11) by designing so as to satisfy the relational expression (6) described above.

Therefore, regardless of the width dimension T [mm] of the blade 27, the Hertz stress Pmax can always be made equal to or less than the numerical value represented by the relational expression (11), the reliability design is facilitated, and the highly reliable compressor 1 is obtained.
Below, the numerical value of an Example is shown in [Table 1].

In Example 3 in [Table 1], the radius Ri of the inner raceway surface M of the roller 23b is made as large as possible within the range satisfying the relational expression (1), and the rolling element 23c having a large diameter is formed. It is designed to be used.
By increasing the diameter of the rolling element 23c in this way, the basic load rating of the rolling bearing 23 is increased, so that design specifications that emphasize the basic load rating can be provided.

In the known example 1 (e.g. JP 2005 No. -140123), polyol esters as refrigerant and a lubricating oil does not contain chlorine in the molecule or be a polyvinyl ether as a base oil, the roller and the vane abnormal wear, The following conditions are disclosed in order to provide a highly reliable rotary compressor that can prevent the above.

That is, a vane having a curvature radius (Rv) (cm) at a sliding contact portion with the roller of the vane is represented by the following expression (A) is used. T <Rv <Rr (A)
Where T is the vane thickness (cm), and Rr is the outer radius of curvature (cm) of the roller in sliding contact with the vane.

Regarding the relational expressions (6) and (7), when comparing the numerical values of the known example 1, the range of the known example 1 is too wide in the range T <Rv <Rr. as shown, large Hertzian stress Pmax relative to examples 1-3, it is understood to include also the reliability is inferior.
Regarding the relational expressions (6) and (7), the surface roughness of the contact surface of the blade 27 with the roller 23b and the outer peripheral surface of the roller 23b is Rz (JIS standard) and is 3.2 μm or less . Select .

  That is, by adopting the compressor 1 having the above structure, the frictional resistance is reduced at the contact surface between the blade 27 and the roller 23b, so that the roller 23b can be easily rotated, and at the same position of the roller inner diameter raceway. Prevents the load from being received and improves the life of the rolling bearing. Therefore, the highly reliable compressor 1 is obtained.

In addition, in the said embodiment, although the cylinder chamber S demonstrated one compressor 1, it is not limited to this, It can apply also to the compressor which has two or more cylinder chambers.
Furthermore, the present invention is not limited to the above-described embodiments as they are, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

  DESCRIPTION OF SYMBOLS 10 ... Sealing case, 11 ... Electric motor part, 13 ... Rotating shaft, 12 ... Compression mechanism part, S ... Cylinder chamber, 20 ... Cylinder, 23b ... Roller (outer ring part), 27 ... Blade, 31 ... Discharge valve mechanism, J ... Back pressure applying means, 23a ... inner ring part, 23c ... rolling element, M ... inner diameter part raceway surface of roller, 1 ... hermetic rotary compressor, 2 ... condenser, 3 ... expansion valve (expansion device), 4 ... evaporation P, refrigerant pipe.

Claims (2)

In the sealed case, an electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft are accommodated,
The compression mechanism includes a cylinder in which a cylinder chamber is formed, a roller that is fitted in an eccentric portion provided in the rotating shaft and performs an eccentric motion in the cylinder chamber, and an outer peripheral surface of the roller that is provided in a reciprocating manner in the cylinder. A discharge valve mechanism that discharges and guides the high-pressure gas compressed in the cylinder chamber into a sealed case;
A back pressure applying means that is provided in the cylinder, guides the high pressure gas discharged from the discharge valve mechanism into the sealed case to the blade rear end, and applies a back pressure to the blade;
In a hermetic rotary compressor equipped with
The inner ring portion of the rolling bearing is fitted to the rotating shaft eccentric portion,
The outer ring portion of the rolling bearing is also used as the roller with which the blade contacts,
The raceway surface of the rolling element interposed between the inner ring portion and the outer ring portion of the rolling bearing is formed on a roller inner diameter portion which is an outer ring inner diameter portion,
The width of the blade is T [mm], the outer radius of the roller is Rr [mm], the outermost radius of the inner raceway surface of the roller is Ri [mm], the Young's modulus of the roller is Er [MPa], The following relational expression (1) is established, where C [mm] is the distance between the moving bodies on the raceway and ΔP [MPa] is the differential pressure between the discharge pressure and the suction pressure during compressor operation. Hermetic rotary compressor.

A refrigeration cycle apparatus comprising the rotary compressor according to claim 1 , a condenser, an expansion device, and an evaporator connected via a refrigerant pipe.

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