JP2010071265A - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide: a rotary compressor inhibiting sliding loss of an eccentric part of a rotary shaft and an eccentric roller, eliminating insufficient stiffness of a rotary shaft connection part, preventing flexible deformation, and improving compression performances; and a refrigeration cycle device provided with the rotary compressor and improving refrigeration cycle device. <P>SOLUTION: In this rotary compressor, expression (1) Rc<Rm+e and expression (2) Rc≥Rs+e are satisfied where eccentric part radius of the rotary shaft is represented by Rc, main shaft part radius by Rm, auxiliary shaft part radius by Rs, and, eccentric quantity of the eccentric part by e, expression (3) (2L-H)/(D+2e)≥0.5 is satisfied where axial length of a connection part is represented by L, shaft diameter of the connection part by (ϕ)D and axial length (thickness) of the eccentric roller by H, and expression (4) (ΔP×Dro×H×L<SP>3</SP>)/(E×M)≤0.02 (mm) is satisfied where differential pressure of delivery pressure and suction pressure is represented by ΔP, outer diameter of the eccentric roller by (ϕ)Dro, Young's modulus of the rotary shaft by E, second moment of area of the connection part by M, and cylinder inner diameter of the connection part by (ϕ)Di. Here, M=πX(D<SP>4</SP>-Di<SP>4</SP>)/64. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary type compressor provided with a plurality of cylinder chambers, and a refrigeration cycle apparatus comprising the rotary compressor and constituting a refrigeration cycle.

The rotary compressor disclosed in [Patent Document 1] is a one-cylinder rotary compressor provided with one compression mechanism, and the inner diameter of the cylinder chamber is Dcy and the cylinder height (axial length). Is H, the shaft diameter of the eccentric portion of the rotating shaft is Dcr, and the axial sliding length (contact length) between the eccentric portion of the rotating shaft and the eccentric roller is L,
H / Dcy ≦ 0.4
L / Dcr ≧ 0.6
It is characterized by having become.
JP 2008-14150 A

  This [Patent Document 1] describes the relationship between the shaft diameter of the eccentric portion of the rotating shaft and the sliding length in the axial direction of the eccentric portion and the eccentric roller in the one-cylinder rotary compressor. Recently, a rotary compressor of a type having a plurality (two) of cylinders is frequently used. In such a two-cylinder type rotary compressor, the above-mentioned relational expression is not necessarily the optimum condition.

  In the two-cylinder type rotary compressor, an eccentric roller that rotates in each cylinder chamber is provided, and each eccentric roller is fitted to an eccentric portion that is formed integrally with a rotary shaft. And the connection part formed between each eccentric part can set the eccentric roller to the eccentric part from the one end side of a rotating shaft by setting the shaft diameter smaller than the shaft diameter of an eccentric part.

  Therefore, when designing the outer diameter and axial length of the eccentric roller and the shaft diameter and axial length of the rotating shaft eccentric part, it is fitted to the rotating shaft eccentric part when actually performing the compression operation. If the suppression of the sliding loss with the eccentric roller is taken into consideration and the prevention of the bending deformation due to the lack of rigidity of the connecting portion formed between the eccentric portions is taken into consideration, there is a risk that the compression performance will be lowered.

  The present invention has been made on the basis of the above circumstances, and the object thereof is the relationship between the shaft diameter of the rotating shaft eccentric part, the sliding length of the eccentric part and the eccentric roller, and the connecting part between the eccentric parts. As a component configuration that takes into account the bending of the shaft, the sliding loss between the eccentric part of the rotating shaft and the eccentric roller is suppressed, the lack of rigidity at the connecting part between the eccentric parts is eliminated, and the deformation performance is prevented and the compression performance is reduced. An object of the present invention is to provide a rotary compressor that can be improved, and a refrigeration cycle apparatus that is provided with this rotary compressor and that can improve the efficiency of the refrigeration cycle.

In order to satisfy the above object, the rotary compressor of the present invention accommodates an electric motor part and a compression mechanism part in a hermetically sealed container, and the compression mechanism part is provided with an intermediate partition plate, and each has an inner diameter part. A plurality of cylinders, a main bearing which is attached to one cylinder and covers the inner diameter part of the cylinder together with the intermediate partition plate and forms a cylinder chamber, and a cylinder chamber which is attached to the other cylinder and covers the inner diameter part of the cylinder together with the intermediate partition plate A sub-bearing that forms a shaft, an eccentric portion that is housed in each cylinder chamber, a main shaft portion that is pivotally supported by the main bearing, a rotary shaft that has a sub-shaft portion that is pivotally supported by the sub-bearing, and is connected to the motor portion, And an eccentric roller that is fitted in each eccentric part of the rotating shaft and is driven to rotate in each cylinder chamber. The eccentric part radius of the rotating shaft is Rc, the main shaft radius of the rotating shaft is Rm, and the auxiliary shaft radius of the rotating shaft is Rs, eccentric part When the eccentricity was e,
Rc <Rm + e (1), Rc ≧ Rs + e (2)
Equations (1) and (2) are satisfied, and the connecting portion between the adjacent eccentric portions is formed in a columnar shape or a cylindrical shape, the axial length of the connecting portion between the eccentric portions is L, and the axial diameter of the connecting portion is When φD and the axial length (thickness) of the eccentric roller are H,
(2L−H) / (D + 2e) ≧ 0.5 (3)
Equation (3) holds, the differential pressure between the discharge pressure and suction pressure during compression operation is ΔP, the outer diameter of the eccentric roller is φDro, the Young's modulus of the rotating shaft is E, the cross-sectional secondary moment of the joint is M, and the eccentric portion When the inner diameter of the connecting portion is φDi,
(ΔP · Dro · H · L ³ ) / (E · M) ≦ 0.02 [mm] (4)
However, M = π · (D ⁴ −Di ⁴ ) / 64 (4) holds.
In order to satisfy the above object, a refrigeration cycle apparatus of the present invention comprises the rotary compressor, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.

  According to the present invention, the sliding loss between the eccentric part of the rotating shaft and the eccentric roller is suppressed, the lack of rigidity at the connecting part between the eccentric parts is eliminated, and the bending deformation is prevented and the compression performance is improved. It is possible to provide an obtained rotary compressor and a refrigeration cycle apparatus provided with the rotary compressor and capable of improving the refrigeration cycle efficiency.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view in which a part of the rotary compressor R is omitted and a refrigeration cycle configuration diagram of a refrigeration cycle apparatus. FIG. 2 is an enlarged longitudinal sectional view of a main part of the rotary compressor. (In order to avoid complications in the drawings, there are parts that are not denoted by reference numerals even if they are explained, and there are parts that are not explained even if they are shown. The same applies hereinafter).
First, the rotary compressor R will be described. 1 is a sealed container, and a compression mechanism section 3 is provided in the lower part of the sealed container 1 and an electric motor section 4 is provided in the upper part. The compression mechanism unit 3 and the motor unit 4 are connected by a rotating shaft 5.

  The compression mechanism section 3 includes a first cylinder 6A on the upper surface portion of the intermediate partition plate 2 via the intermediate partition plate 2 and a second cylinder 6B on the lower surface portion. Further, the main bearing 7 is attached and fixed to the upper surface of the first cylinder 6A, and the auxiliary bearing 8 is attached and fixed to the lower surface of the second cylinder 6B.

  The main bearing 7 supports the main shaft portion 5 a of the rotating shaft 5, and the auxiliary bearing 8 supports the auxiliary shaft portion 5 b of the rotating shaft 5. The rotating shaft 5 penetrates through the first and second cylinders 6A and 6B, and integrally includes a first eccentric part a and a second eccentric part b formed with a phase difference of about 180 °. Yes.

  The first and second eccentric parts a and b have the same diameter as each other and are assembled so as to be positioned at the inner diameter parts of the first and second cylinders 6A and 6B. A first eccentric roller 9a is fitted to the peripheral surface of the first eccentric part a, and a second eccentric roller 9b is fitted to the peripheral surface of the second eccentric part b.

  An inner diameter portion of the first cylinder 6A is surrounded by the main bearing 7 and the intermediate partition plate 2, and a first cylinder chamber Sa is formed. The inner diameter portion of the second cylinder 6B is surrounded by the auxiliary bearing 8 and the intermediate partition plate 2, and a second cylinder chamber Sb is formed.

  The cylinder chambers Sa and Sb are formed to have the same diameter and height, and a part of the peripheral wall of the eccentric rollers 9a and 9b is accommodated so as to be eccentrically rotatable while being in line contact with a part of the peripheral wall of the cylinder chambers Sa and Sb. The

  Although not particularly illustrated, the first cylinder 6A is provided with a vane chamber communicating with the first cylinder chamber Sa, and the vane is movably accommodated therein. The second cylinder 6B is provided with a vane chamber communicating with the second cylinder chamber Sb, and the vane is movably accommodated therein.

  The tip of each vane is formed in a semicircular shape in a plan view, protrudes into the opposing cylinder chambers Sa and Sb, and has a circular shape in the plan view in the first and second eccentric rollers 9a and 9b. Line contact is possible regardless of this rotation angle.

  A lateral hole that communicates the vane chamber of the first cylinder 6A and the outer peripheral surface of the cylinder 6A is provided, and a spring member that is a compression spring is accommodated. This spring member is interposed between the rear end side end face of the vane and the inner peripheral wall of the sealed container 1, and applies an elastic force (back pressure) to the vane.

  A horizontal hole that communicates the vane chamber of the second cylinder 6B and the outer peripheral surface of the cylinder 6B is provided, and a spring member that is a compression spring is accommodated. This spring member is interposed between the rear end side end face of the vane and the inner peripheral wall of the sealed container 1, and applies an elastic force (back pressure) to the vane.

  On the other hand, a refrigerant pipe P is connected to the upper end portion of the sealed case 1, and this refrigerant pipe P is connected to an accumulator (not shown) via a condenser 15, an expansion device 16, and an evaporator 17.

Furthermore, from the accumulator, a first suction refrigerant pipe Pa that passes through the sealed case 1 of the rotary compressor R and the side of the first cylinder 6A and directly communicates with the first cylinder chamber Sa, and the sealed case 1 And a second suction refrigerant pipe Pb that passes through the side of the second cylinder 6B and communicates directly with the second cylinder chamber Sb.
In this way, the refrigeration cycle of the refrigeration cycle apparatus is configured.

Next, the operation of the refrigeration cycle apparatus including the rotary compressor R described above will be described.
When an instruction to start operation is input, the control unit sends an operation signal to the motor unit 4 via the inverter. The rotary shaft 5 is rotationally driven, and the first and second eccentric rollers 9a and 9b simultaneously perform eccentric rotation in the first and second cylinder chambers Sa and Sb.

  In the first cylinder 6A, since the vane is always elastically pressed and urged by the spring member, the tip edge of the vane is slidably contacted with the peripheral wall of the first eccentric roller 9a so as to move inside the first cylinder chamber Sa. Divide into suction chamber and compression chamber.

  The first cylinder chamber Sa inner surface rolling contact position on the circumferential surface of the first eccentric roller 9a coincides with the vane tip position, and the space capacity of the first cylinder chamber Sa is in a state where the vane is most retracted. Maximum. The refrigerant gas is sucked into the first cylinder chamber Sa from the accumulator through the refrigerant pipe Pa to be filled.

  With the eccentric rotation of the first eccentric roller 9a, the rolling contact position of the first eccentric roller 9a with the inner peripheral surface of the first cylinder chamber Sa moves, and the first cylinder chamber Sa is partitioned. The volume of the compression chamber is reduced. That is, the gas previously introduced into the first cylinder chamber Sa is gradually compressed.

  The rotary shaft 5 is continuously rotated, the capacity of the compression chamber partitioned into the first cylinder chamber Sa is further reduced, the gas is compressed, and the discharge valve is opened when the pressure rises to a predetermined pressure. The high-pressure gas is discharged into the sealed case 1 through the valve cover and fills up. And it discharges from the refrigerant | coolant pipe | tube P connected to the airtight case 1 upper part.

  On the other hand, since the second eccentric portion 9b is provided at a position that is 180 ° out of phase with respect to the first eccentric portion 9a, in the first cylinder chamber Sa accompanying the eccentric rotation of the first eccentric portion 9a. The compression action is performed with a phase difference of 180 ° in the second cylinder chamber Sb in accordance with the eccentric action of the second eccentric part 9b and the eccentric rotation of the second eccentric part 9b.

  In any of the cylinder chambers Sa and Sb, the compressed high-pressure gas is discharged into the sealed case 1 through the valve cover, and is mixed and filled. The high-pressure gas is discharged from the rotary compressor R to the refrigerant pipe P and guided to the condenser 15, where it is condensed and liquefied by exchanging heat with the outside air or water. This liquid refrigerant is led to the expansion device 16 and adiabatically expands, and is led to the evaporator 17 to take away the latent heat of evaporation from the heat exchange air and perform a refrigeration action.

  The refrigerant evaporated in the evaporator 17 is led to an accumulator and separated into gas and liquid, and only the evaporated refrigerant passes through the suction refrigerant pipes Pa and Pb and the first cylinder chamber Sa and the second cylinder chamber Sb in the rotary compressor R. Sucked into. Then, the above action is performed again, and the above path is circulated.

In the rotary compressor R provided in such a refrigeration cycle apparatus, the radii of eccentric parts a and b of the rotating shaft 5 are Rc, the radius of the main shaft part 5a of the rotating shaft 5 is Rm, and the radius of the auxiliary shaft part 5b of the rotating shaft 5 is Rm. When the eccentric amount of Rs and eccentric parts a and b is e,
Rc <Rm + e (1)
Rc ≧ Rs + e (2)
It is designed so that the expressions (1) and (2) are established.

The connecting portion 10 formed between the adjacent first eccentric portion a and the second eccentric portion b is formed in a columnar shape or a cylindrical shape. When the axial length of the connecting portion 10 is L, the axial diameter of the connecting portion 10 is φD, and the axial lengths (thicknesses) of the eccentric rollers 9a and 9b are H,
(2L−H) / (D + 2e) ≧ 0.5 (3)
(3) It is designed so that Formula may be formed.

  FIG. 4 is a characteristic diagram of the sliding length Lcr of each of the eccentric parts a and b and the eccentric rollers 9a and 9b / the diameter φDcr of the eccentric parts a and b and the sliding loss of the eccentric parts a and b. There is a relationship such as McKee's empirical formula.

  4 illustrates that the diameter of the eccentric parts a and b of the rotary shaft 5 is φDcr, the sliding length between the eccentric parts a and b and the eccentric rollers 9a and 9b is Lcr, and Lcr / φDcr is the horizontal axis. The vertical axis represents the sliding loss of the eccentric parts a and b.

  As a result, if Lcr / φDcr is larger than 0.5, the sliding loss at the sliding portions a and b of the rotating shaft 5 can be reduced, but the rotating shaft 5 can be reduced within a range where Lcr / φDcr is smaller than 0.5. It can be seen that the sliding loss at the sliding portions a and b greatly increases.

  Further, as described above, in the configuration of the rotary compressor R that includes the plurality of cylinders 6A and 6B and the eccentric portions a and b of the rotating shaft 5 are accommodated in the cylinder chambers Sa and Sb, the eccentric portions a and b are provided. On the other hand, in order to smoothly perform the operation of fitting the eccentric rollers 9a and 9b, it is necessary to make an optimum design.

FIGS. 3A to 3D are diagrams sequentially illustrating a process of fitting the first eccentric roller 9a to the first eccentric portion a provided on the main shaft portion 5a side of the rotating shaft 5. FIG.
As shown in FIG. 3A, for example, the first eccentric portion a protrudes to the left side of the drawing relative to the central axis CL of the rotating shaft 5, and the second eccentric portion b protrudes to the right side of the drawing and holds it. As a state before this figure, after inserting the first eccentric roller 9a from the end of the rotary shaft 5 on the side of the auxiliary shaft portion 5b and passing through the auxiliary shaft portion 5b, the first eccentric roller 9a is moved as shown in the drawing. Fit into the second eccentric part b.

  The second eccentric portion b is eccentric from the central axis CL of the rotating shaft 5 by an eccentric amount e. When the radius of the second eccentric portion b is Rc, the diameter of the inner diameter portion of the first eccentric roller 9a fitted therein is 2Rc.

  Further, the anti-eccentric side circumferential surface position in the second eccentric part b and the circumferential surface part of the connecting part 10 are formed to coincide with each other, and the anti-eccentric side circumferential surface position in the first eccentric part a; It forms so that a part of peripheral surface of the connection part 10 may correspond.

  As shown in FIGS. 3A to 3B, the first eccentric roller 9a is extracted from the second eccentric portion b, and once between the first eccentric portion a and the second eccentric portion b. The first eccentric roller 9a is moved so that the first eccentric roller 9a is positioned at the connecting portion 10 formed in the above.

  In this state, the axial length (thickness) H of the first eccentric roller 9a> the axial length L of the connecting portion 10 is configured. Therefore, if the chamfered portions q are not provided at both end portions in the axial direction at the inner diameter portion of the first eccentric roller 9a, the first eccentric roller a cannot be moved any further.

  The chamfered portion q provided in this way must be set to have an axial length of (HL) or more. Therefore, the length obtained by subtracting the total length 2 (HL) of the two chamfered portions q from the axial length H of the first eccentric roller 9a is the sliding length of the first eccentric roller 9a. Secured.

  Specifically, the sliding length of the first eccentric roller 9a is H-2 (HL), and when this is developed, it becomes 2L-H or less. Naturally, the axial length of the first eccentric portion a in which the first eccentric roller 9a is fitted and slides relative to each other, that is, the sliding length with respect to the first eccentric roller 9a is also 2L-H.

  From the state of FIG. 3B, the first eccentric roller 9a is tilted counterclockwise as indicated by an arrow in the figure. When the first eccentric roller 9a is moved in the left direction in the figure as it is, the chamfered portion q provided on the inner diameter portion of the first eccentric roller 9a gets over the upper end corner of the second eccentric portion b.

Further, by moving the first eccentric roller 9a in the left direction in the figure, the lower end surface of the first eccentric roller 9a slides in contact with the upper end surface of the second eccentric portion b, and the first eccentric roller 9b The upper end surface slides in contact with the lower end surface of the first eccentric part a.
Finally, as shown in FIG. 3C, the first eccentric roller 9a is placed on the upper end surface of the second eccentric portion b, and the inner diameter portion of the first eccentric roller 9a and the first eccentric portion a. Opposite to the eccentric circumferential surface.

Next, as shown in FIG. 3D, the first eccentric roller 9a is fitted into the first eccentric portion a by shifting the first eccentric roller 9a upward.
At this time, since the first eccentric roller 9a cannot be assembled to the first eccentric portion a unless the shaft diameter of the first eccentric portion a is equal to or greater than D + 2e, the first eccentric portion described above with reference to FIG. The relationship of the sliding length Lcr / shaft diameter φDcr of a is (2L−H) / (D + 2e) or less.

Furthermore, since Lcr / φDcr ≧ 0.5 is derived from FIG.
(2L−H) / (D + 2e) ≧ 0.5 (3)
By adopting a configuration in which the relationship of the above-described expression (3) is established, a significant increase in sliding loss between the first and second eccentric portions a and b and the first and second eccentric rollers 9a and 9b is suppressed. Thus, a rotary compressor R having high performance can be provided.

Furthermore, the differential pressure between the discharge pressure and the suction pressure in the rotary compressor R during the compression operation is ΔP, the outer diameters of the first and second eccentric rollers 9a and 9b are φDro, and the Young's modulus of the rotating shaft 5 is E , Where M is the moment of inertia of the cross section of the connecting part 10 between the eccentric parts a and b,
(ΔP · Dro · H · L ³ ) / (E · M) ≦ 0.02 [mm] (4)
(4) By comprising so that Formula may be satisfied, the bending deformation of the connection part 10 between the eccentric parts a and b is prevented, and the improvement of compression performance can be obtained.
However, M = π · (D4−Di ⁴ ) / 64, and Di is the inner diameter of the cylindrical connecting portion 10 between the eccentric portions a and b.

To explain, when a load F acts on the tip of a cantilever having a length L, a Young's modulus E, a secondary moment M and a constant cross-sectional area, the deflection σ of the tip of the cantilever is
σ = (F · L ³ ) / (3 · E · M) (5)
It is known that equation (5) holds.
Also in the connecting portion 10, the amount of deflection due to the gas load in one of the cylinder chambers Sa or Sb is considered to be proportional to (ΔP · Dro · H · L ³ ) / (E · M).

FIG. 5 is a relationship diagram between (ΔP · Dro · H · L ³ ) / (E · M) and CPO under specific conditions.
From FIG. 5, when (ΔP · Dro · H · L ³ ) / (E · M) increases, the clearance increases due to the bending deformation of the connecting portion 10 formed between the eccentric portions a and b of the rotating shaft 5. It can be seen that the compression performance deteriorates.

In particular, when (ΔP · Dro · H · L ³ ) / (E · M)> 2 [mm], there is a decrease in compression performance due to the occurrence of bending deformation at the connecting portion 10.
Therefore, the equation (4) described above is obtained.
(ΔP · Dro · H · L ³ ) / (E · M) ≦ 0.02 [mm] (4)
However, M = π · (D4−Di ⁴ ) / 64 and Di is the inner diameter of the cylindrical connecting portion 10.
By adopting the configuration that satisfies the formula (4), it is possible to prevent the compression performance from being lowered due to the bending deformation due to insufficient rigidity in the connecting portion 10 and to improve the compression performance.

[Table 1] below is a specific design example that satisfies the equation (4).

The COPo shown on the vertical axis in FIG. 5 is the COP value at (ΔP · Dro · H · L ³ ) / (E · M) = 0.0137 in [Table 1].

Further, if (ΔP · Dro · H · L ³ ) / (E · M) is 0.02 [mm] or less, it is possible to prevent the compression performance from being lowered due to the bending deformation of the connecting portion 10 as shown in FIG. However, as the value of (ΔP · Dro · H · L ³ ) / (E · M) decreases, the value of (2L−H) / (D + 2e) decreases.

However, when (ΔP · Dro · H · L ³ ) / (E · M) is 0.01 [mm] or more, the condition (2L−H) (D + 2e) ≧ 0.5 is satisfied in many conditions. It is possible.

In conclusion, more preferably,
(ΔP · Dro · H · L ³ ) / (E · M) ≧ 0.01 [mm] (5)
(5) What is necessary is just to comprise so that Formula may be formed.

  Note that the present invention is not limited to the above-described embodiment as it is, 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.

The schematic longitudinal cross-sectional view of the rotary compressor based on one embodiment in this invention, and the refrigerating cycle block diagram of a refrigerating cycle apparatus. The expanded longitudinal cross-sectional view of the 2-cylinder rotary compressor principal part which concerns on the same embodiment. The figure which shows in order the process of incorporating a 1st eccentric roller in the 1st eccentric part of the rotating shaft based on the embodiment. The characteristic figure of the eccentric part sliding loss with respect to the eccentric part sliding length / eccentric part axial diameter based on the embodiment. According to the embodiment, the characteristic diagram of COP for ^{(ΔP · Dro · H · L} 3) / (E · M).

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Airtight container, 4 ... Electric motor part, 3 ... Compression mechanism part, 2 ... Intermediate partition plate, 6A ... 1st cylinder, 6B ... 2nd cylinder, Sa ... 1st cylinder chamber, Sb ... 2nd Cylinder chamber, 7 ... main bearing, 8 ... sub bearing, a ... first eccentric portion, b ... second eccentric portion, 5a ... main shaft portion, 5b ... sub shaft portion, 5 ... rotating shaft, 9a ... first Eccentric roller, 9b ... second eccentric roller, R ... rotary compressor, 10 ... connecting portion, 15 ... condenser, 16 ... expansion device, 17 ... evaporator.

Claims (3)

The motor part and the compression mechanism part are accommodated in the sealed container,
The compression mechanism is
A plurality of cylinders provided with intermediate partition plates, each having an inner diameter portion;
A main bearing attached to the one cylinder and covering the inner diameter part of the one cylinder together with the intermediate partition plate to form a first cylinder chamber;
A secondary bearing mounted on the other cylinder and covering the inner diameter of the other cylinder together with the intermediate partition plate to form a second cylinder chamber;
An electric motor portion having an eccentric portion accommodated in each of the first cylinder chamber and the second cylinder chamber, a main shaft portion pivotally supported by the main bearing, and a subshaft portion pivotally supported by the auxiliary bearing; A rotating shaft coupled to
An eccentric roller fitted into each of the eccentric portions of the rotating shaft and driven to rotate in the first cylinder chamber and the second cylinder chamber;
In the rotary compressor comprising:
When the eccentric portion radius of the rotating shaft is Rc, the main shaft radius of the rotating shaft is Rm, the auxiliary shaft radius of the rotating shaft is Rs, and the eccentric amount of the eccentric portion is e,
Rc <Rm + e (1)
Rc ≧ Rs + e (2)
(1) Formula and (2) Formula hold | maintained, and the connection part between adjacent eccentric parts is formed in column shape or cylindrical shape,
When the axial length of the connecting portion is L, the shaft diameter of the connecting portion is φD, and the axial length (thickness) of the eccentric roller is H,
(2L−H) / (D + 2e) ≧ 0.5 (3)
Equation (3) holds,
When the differential pressure between the discharge pressure and the suction pressure during the compression operation is ΔP, the outer diameter of the eccentric roller is φDro, the Young's modulus of the rotating shaft is E, and the secondary moment of the section of the connecting portion is M,
(ΔP · Dro · H · L ³ ) / (E · M) ≦ 0.02 [mm] (4)
(4) A rotary compressor characterized in that the formula is satisfied.
However, M = π · (D ⁴ −Di ⁴ ) / 64
Di: Inner diameter of cylindrical connecting part More preferably,
(ΔP · Dro · H · L ³ ) / (E · M) ≧ 0.01 [mm] (5)
The rotary compressor according to claim 1, wherein the formula (5) is established.   A refrigeration cycle apparatus comprising the rotary compressor according to any one of claims 1 and 2, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.

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