JP6350843B1 - Rotary shaft of rotary compressor and rotary compressor - Google Patents

Abstract

A rotary shaft of a rotary compressor and a rotary compressor capable of improving the efficiency by suppressing the deflection of the rotary shaft are provided. An intermediate shaft portion of a rotating shaft is convex in a direction intersecting with an eccentric direction of a main shaft piston rotor and a sub-shaft piston rotor when viewed in a cross section perpendicular to an axis. On the outer peripheral surface, and the apex 17a is rearward in the rotational direction R with respect to a virtual line Y passing through the axis O perpendicular to the eccentric direction. It is arranged at a position shifted by an angle α larger than 0 degree and smaller than 45 degrees. [Selection] Figure 3

Description

  The present invention relates to a rotary shaft of a rotary compressor that compresses a fluid, and a rotary compressor including the rotary shaft.

  Conventionally, a rotary compressor applied to a refrigeration cycle such as an air conditioner is known. In such a rotary compressor, a casing is mainly provided with a rotating shaft, a bearing that supports the rotating shaft, a piston rotor that is eccentrically attached to the rotating shaft, and a cylinder in which the piston rotor is disposed. ing. In the rotary compressor, the fluid (refrigerant) that flows into the cylinder by the rotation of the piston rotor is compressed.

  In recent years, there has been an increasing demand for high efficiency in rotary compressors. For this reason, attempts have been made to reduce the size of the piston in order to increase the displacement of the piston. However, in this case, there is a problem that the load acting on the piston is increased and the rotating shaft is easily bent.

JP 2013-181420 A

  For example, in Patent Document 1, the bending of the rotating shaft is suppressed using a technique such as reducing the span between the main shaft portion and the sub shaft portion of the rotating shaft, but the cross-sectional shape of the rotating shaft is optimized. Thus, a method of suppressing the deflection of the rotating shaft can be considered.

  The present invention provides a rotary shaft of a rotary compressor and a rotary compressor capable of increasing the efficiency by suppressing the deflection of the rotary shaft.

The rotary shaft of the rotary compressor according to one aspect of the present invention is rotatably supported with respect to the casing having the compression chamber inside, and can be compressed with the lubricating oil by being driven to rotate about the axis. A rotary shaft of the rotary compressor, the shaft main body extending in a rod shape around the axis, the main shaft piston rotor being eccentrically provided in the shaft main body and accommodated in the first compression chamber of the compression chamber; The main shaft piston rotor is disposed away from the main shaft piston rotor in the direction of the axis, and is provided eccentrically with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. And an intermediate shaft portion provided in the shaft main body at a position sandwiched between the main shaft piston rotor and the sub shaft piston rotor. The intermediate shaft portion is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor when viewed in a cross section orthogonal to the axis, and the outer peripheral surface of the intermediate shaft portion The top portion having the largest distance to the axis line is provided on the outer peripheral surface, the top portions are provided in pairs symmetrically across the axis line, and the intermediate shaft portion is seen in a cross section orthogonal to the axis line. In the meantime, the intermediate shaft portion is partly in a radial inner side from a region where the outer peripheral edge of the main shaft piston rotor and the outer peripheral edge of the sub shaft piston rotor overlap each other only in the front side portion in the rotational direction of the top portion. The top portion has a shape that is cut away toward the center of the imaginary line, and the top portion is 45 degrees greater than 0 degree on the rear side in the rotational direction with respect to a virtual line that passes through the axis perpendicular to the eccentric direction. In a position shifted by a smaller angle It is location.

According to the rotary shaft of such a rotary compressor, the top portion of the intermediate shaft portion is displaced at an angle larger than 0 degree and smaller than 45 degrees on the rear side in the rotational direction with respect to a virtual line passing through the axis line perpendicular to the eccentric direction. It is arranged at the position. That is, the top portion is not arranged on the imaginary line passing through the axis perpendicular to the eccentric direction, and the diameter of the intermediate shaft portion is the largest at a position shifted to the rear side in the rotation direction with respect to the imaginary line. Therefore, the cross-sectional secondary moment of the intermediate shaft portion can be increased at the position where the top portion is provided, and the rigidity of the intermediate shaft portion can be improved.
Here, it was found that the maximum load during compression acts on the intermediate shaft portion in the range of more than 5 degrees and less than 41 degrees from the imaginary line to the rear side in the rotation direction. In this aspect, the top portion is arranged at a position shifted by an angle larger than 0 degrees and smaller than 45 degrees on the rear side in the rotation direction with respect to the imaginary line, and the rigidity is higher at this position. Even if the thickness of the intermediate shaft portion on the front side of the is thinner than that of the columnar shape, sufficient strength can be secured. Therefore, it is possible to ensure the strength while reducing the weight of the intermediate shaft portion. Therefore, even when a compression load from each piston rotor acts on the rotation shaft, it is possible to suppress the bending deformation of the rotation shaft.
In the rotary shaft of the rotary compressor, a pair of the top portions are provided at symmetrical positions with the axis line interposed therebetween. By providing the tops at symmetrical positions in this way, it is possible to smoothly guide the lubricating oil while ensuring the strength of the intermediate shaft portion, and to further reduce the stirring loss during rotation of the rotating shaft. Furthermore, the centrifugal force acting on the position of the top portion of the intermediate shaft portion during rotation can be canceled out by the pair of top portions, and the stability during rotation of the rotating shaft can be improved.

  Further, in the rotary shaft of the rotary compressor, when viewed in a cross section orthogonal to the axis, the outer peripheral surface of the intermediate shaft portion is an outer peripheral edge of the main shaft piston rotor and an outer peripheral edge of the auxiliary shaft piston rotor. May be arranged in a region where the two overlap.

  According to such a configuration, the top portion is formed by scraping the outer peripheral surface of the intermediate shaft portion on the front side in the rotational direction of the top portion. Therefore, when the rotating shaft rotates, the lubricating oil around the intermediate shaft portion is smoothly guided toward the top of the intermediate shaft portion, and smoothly flows along the outer peripheral surface of the intermediate shaft portion toward the rear in the rotation direction. To do. Therefore, it is possible to reduce the stirring loss of the lubricating oil.

The rotary shaft of the rotary compressor according to one aspect of the present invention is rotatably supported with respect to the casing having the compression chamber inside, and can be compressed with the lubricating oil by being driven to rotate about the axis. A rotary shaft of the rotary compressor, the shaft main body extending in a rod shape around the axis, the main shaft piston rotor being eccentrically provided in the shaft main body and accommodated in the first compression chamber of the compression chamber; The main shaft piston rotor is disposed away from the main shaft piston rotor in the direction of the axis, and is provided eccentrically with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. And an intermediate shaft portion provided in the shaft main body at a position sandwiched between the main shaft piston rotor and the sub shaft piston rotor. The intermediate shaft portion is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor when viewed in a cross section orthogonal to the axis, and the outer peripheral surface of the intermediate shaft portion The top portion having the largest distance to the axis line is provided on the outer peripheral surface, and when viewed in a cross section perpendicular to the axis line, the outer peripheral surface of the intermediate shaft portion is connected to the outer peripheral edge of the main shaft piston rotor and the sub-axis. It is arranged in a region where the outer peripheral edge of the axial piston rotor overlaps, and the top portion is greater than 0 degree and more than 5 degrees on the rear side in the rotational direction with respect to a virtual line passing through the axis line perpendicular to the eccentric direction. that it is located in offset at a small angle position.

  According to such a configuration, the top portion is formed by scraping the outer peripheral surface of the intermediate shaft portion on the front side in the rotational direction of the top portion. Thus, the diameter of the intermediate shaft portion is not extremely reduced, and the strength of the intermediate shaft portion can be sufficiently secured.

  Further, in the rotary shaft of the rotary compressor described above, the outer peripheral surface of the intermediate shaft portion is disposed inside the outer edge of the one region and is convex in a direction away from the axis from the top toward the front in the rotation direction. A curved surface that extends in a curved manner, and continues smoothly to the curved surface on the top side, and is provided at a position including an intersection of an imaginary line extending in the eccentric direction and an outer edge of the one region, along the outer edge of the one region. And an eccentric-side curved surface that extends.

  By providing the top side curved surface and the eccentric side curved surface as the outer peripheral surface of the intermediate shaft portion in this way, the outer surface of the intermediate shaft portion is smooth toward the top from the position of the above intersection at the front side in the rotational direction than the top portion. A curved surface is formed. Therefore, when the lubricating oil is agitated by the rotating shaft, it smoothly flows from the eccentric curved surface toward the top curved surface. Therefore, even if it is the intermediate shaft part which has a top part, the stirring loss of lubricating oil can be reduced.

The rotary shaft of the rotary compressor according to one aspect of the present invention is rotatably supported with respect to the casing having the compression chamber inside, and can be compressed with the lubricating oil by being driven to rotate about the axis. A rotary shaft of the rotary compressor, the shaft main body extending in a rod shape around the axis, the main shaft piston rotor being eccentrically provided in the shaft main body and accommodated in the first compression chamber of the compression chamber; The main shaft piston rotor is disposed away from the main shaft piston rotor in the direction of the axis, and is provided eccentrically with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. And an intermediate shaft portion provided in the shaft main body at a position sandwiched between the main shaft piston rotor and the sub shaft piston rotor. The intermediate shaft portion is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor when viewed in a cross section orthogonal to the axis, and the outer peripheral surface of the intermediate shaft portion On the outer peripheral surface, the apex having the largest distance from the axis is on the outer peripheral surface, and the apex is at 0 degrees on the rear side in the rotational direction with respect to the virtual line passing through the axis perpendicular to the eccentric direction. The tops are arranged at positions shifted by an angle of less than 45 degrees, and a pair of the tops are provided at symmetrical positions across the axis, and each of the tops has a rotational direction relative to a direction orthogonal to the eccentric direction. amount of deviation of the angle of the rearward side that differ from each other.

  Even in such a case, it is possible to smoothly guide the lubricating oil while ensuring the strength of the intermediate shaft portion, and to reduce stirring loss during rotation of the rotating shaft.

  In addition, a rotary compressor according to an aspect of the present invention includes the rotary shaft, a drive unit that rotationally drives the rotary shaft, the rotary shaft and the drive unit, and the first compression chamber and A casing having the second compression chamber inside.

  According to such a rotary compressor, by providing the above rotating shaft, the lubricating oil around the intermediate shaft portion is smoothly guided toward the top of the intermediate shaft portion when the rotating shaft rotates, and the rotation direction It is possible to smoothly circulate the outer peripheral surface of the intermediate shaft portion toward the rear of the shaft, and to reduce the stirring loss of the lubricating oil. Compared with the case where the top portion is not provided, it is possible to increase the cross-sectional secondary moment of the intermediate shaft portion, and it is possible to suppress the bending deformation of the rotating shaft.

  According to the rotary shaft of the rotary compressor and the rotary compressor described above, the above configuration can suppress the deflection of the rotary shaft and increase the efficiency.

It is a longitudinal cross-sectional view of the rotary compressor which concerns on embodiment of this invention. It is a figure which shows the rotating shaft of the rotary compressor which concerns on embodiment of this invention. It is sectional drawing which shows the intermediate shaft part in the rotating shaft of the rotary compressor which concerns on embodiment of this invention, Comprising: It is a figure which shows the AA cross section of FIG. In the embodiment of the present invention, (a) shows the relationship between the load direction (maximum gas load direction) of refrigerant gas during compression acting on the rotary shaft of the rotary compressor and the load (maximum gas load) due to the refrigerant gas. It is a graph of an experimental result, (b) is a graph of the experimental result which shows the relationship between the angle (alpha) made with the virtual line Y of the top, and pressure ratio HP / LP. It is sectional drawing which shows the intermediate shaft part in the rotating shaft of the rotary compressor which concerns on the 1st modification of embodiment of this invention. It is sectional drawing which shows the intermediate shaft part in the rotating shaft of the rotary compressor which concerns on the 2nd modification of embodiment of this invention.

Hereinafter, the rotary compressor 1 which concerns on embodiment of this invention is demonstrated.
As shown in FIG. 1, the rotary compressor 1 includes a drive unit 18, a rotary shaft 15 that is rotationally driven by the drive unit 18, and a casing 11 that houses the drive unit 18 and the rotary shaft 15. This rotary compressor 1 is a so-called two-cylinder type rotary compressor 1 in which a compression chamber S is provided in two upper and lower stages inside the casing 11.

The casing 11 has a cylindrical shape centered on the axis O, and two disk-shaped cylinders 12A and 12B are provided at the inner lower portion of the casing 11 with an interval in the vertical direction. The upper cylinder is a main shaft side cylinder 12A, and the lower cylinder is a sub shaft side cylinder 12B.
Cylindrical cylinder inner wall surfaces 12S1 and 12S2 are formed in the cylinders 12A and 12B, respectively. A first compression chamber S1 is defined by the cylinder inner wall surface 12S1 of the main shaft side cylinder 12A, and a second compression chamber S2 is defined by the cylinder inner wall surface 12S2 of the sub shaft side cylinder 12B. A disc-shaped partition plate 10 is provided between the upper and lower cylinders 12A and 12B. The partition plate 10 partitions the first compression chamber S1 and the second compression chamber S2.

  Openings 22 </ b> A and 22 </ b> B are formed on the side surface of the casing 11, that is, the outer peripheral surface, at positions facing the outer peripheral surfaces of the main shaft side cylinder 12 </ b> A and the sub shaft side cylinder 12 </ b> B. In each cylinder 12A, 12B, suction ports 23A, 23B communicating with the first compression chamber S1 and the second compression chamber S2 are formed at positions facing the openings 22A, 22B.

  An accumulator 24 for gas-liquid separation of the refrigerant taken in from the upper suction port 24 a is fixed to the casing 11 via a stay 25 before introducing the refrigerant (fluid) into the casing 11. The accumulator 24 is provided with suction pipes 26 </ b> A and 26 </ b> B for introducing the gas phase of the refrigerant gas-liquid separated by the accumulator 24 into the first compression chamber S <b> 1 and the second compression chamber S <b> 2 in the casing 11. The distal ends of the suction pipes 26A and 26B are connected to the suction ports 23A and 23B through the openings 22A and 22B.

  A discharge port 27 through which the refrigerant compressed in the first compression chamber S1 and the second compression chamber S2 is discharged is provided in the upper part of the casing 11.

  The drive unit 18 is an electric motor, and includes a stator 20 that is fixed to the inner surface of the casing 11 above the spindle-side cylinder 12A, and a rotor 19 that is disposed inside the stator 20 so as to face the stator 20. ing.

  As shown in FIG. 2, the rotary shaft 15 includes a shaft main body 16 having a rod shape extending in the direction of the axis O around the axis O, a main shaft piston rotor 14 </ b> A and a sub shaft piston rotor 14 </ b> B provided on the shaft main body 16, and a main shaft. An intermediate shaft portion 17 disposed at a position sandwiched between the piston rotor 14A and the auxiliary shaft piston rotor 14B in the direction of the axis O is provided.

  The shaft body 16 is provided by being fitted into the rotor 19 of the drive unit 18, and rotates around the axis O together with the rotor 19 by supplying power to the drive unit 18. The shaft body 16 is rotatably supported by the casing 11 by an upper bearing 17A provided at the upper portion of the main shaft side cylinder 12A and a lower bearing 17B provided at the lower portion of the sub shaft side cylinder 12B.

  The main shaft piston rotor 14 </ b> A is provided in the shaft main body 16 and is accommodated in the first compression chamber S <b> 1, and rotates around the axis O together with the shaft main body 16. The main shaft piston rotor 14A is integrally formed with the shaft main body 16, and is externally fitted to a main shaft side eccentric shaft portion 13A having a cylindrical shape centering on an eccentric shaft O1 parallel to the axis O, and has an annular shape. . Thereby, the main shaft piston rotor 14 </ b> A rotates eccentrically with respect to the shaft main body 16 when the shaft main body 16 rotates.

The sub-shaft piston rotor 14 </ b> B is provided in the shaft body 16 and is accommodated in the second compression chamber S <b> 2, and rotates about the axis O together with the shaft body 16. The sub-shaft piston rotor 14B is integrally formed with the shaft body 16 and is externally fitted to a sub-shaft side eccentric shaft portion 13B having a cylindrical shape centering on an eccentric shaft O2 parallel to the axis O and the eccentric shaft O1. It has a ring shape. The eccentric shaft O2 is disposed at a position symmetrical to the eccentric shaft O1 across the axis O.
That is, the main shaft piston rotor 14A and the sub shaft piston rotor 14B rotate in a state of being eccentric in directions different from each other by 180 degrees with respect to the shaft main body 16.

  Here, the rotary shaft 15 may be formed by separately manufacturing a main shaft portion provided with the main shaft piston rotor 14A and a sub shaft portion provided with the sub shaft piston rotor 14B and joining them together, or formed integrally. May be. The main shaft portion and the sub shaft portion may have different outer diameters.

Next, the intermediate shaft portion 17 will be described.
As shown in FIG. 2, the intermediate shaft portion 17 is provided at a position sandwiched between the main shaft piston rotor 14 </ b> A and the auxiliary shaft piston rotor 14 </ b> B in the direction of the axis O. That is, the intermediate shaft portion 17 is disposed in the casing 11 between the main shaft side cylinder 12A and the sub shaft side cylinder 12B.

  As shown in FIG. 3, when the intermediate shaft portion 17 is viewed in a cross section perpendicular to the axis O, the outer peripheral surface of the intermediate shaft portion 17 is the outer peripheral edge 14Aa of the main piston piston rotor 14A and the outer peripheral edge of the sub-shaft piston rotor 14B. It is arranged in one area AR where 14Ba overlaps. More specifically, in the present embodiment, the outer peripheral edge 13Aa of the main shaft side eccentric shaft portion 13A and the outer peripheral edge 13Ba of the sub shaft side eccentric shaft portion 13B are arranged in an overlapping region.

  That is, the cross-sectional shape of the intermediate shaft portion 17 is substantially oval, rugby ball, or almond. As a result, the intermediate shaft portion 17 protrudes on both sides in the direction intersecting the eccentric direction, which is the direction in which the virtual line X connecting the eccentric shafts O1, O2 and the axis O extends over the entire region in the direction of the axis O. It has the top part 17a.

  The pair of top portions 17a are provided at positions that are symmetrical with respect to the axis O. Each top portion 17a is arranged at a position shifted by an angle α on the rear side in the rotation direction R of the rotation shaft 15 with respect to a virtual line Y extending in a direction orthogonal to the eccentric direction. The outer diameter of the intermediate shaft portion 17 is the largest. Further, the outer diameter of the intermediate shaft portion 17 is the smallest in the eccentric direction.

  The outer peripheral surface of the top portion 17a is arranged at a position away from the outer peripheral edges 13Aa and 13Ba which are outer edges of the one area AR, that is, radially inward from the outer edge, and from the axis O toward the front in the rotational direction R from the top portion 17a. It has an arcuate apex-side curved surface 17b that curves convexly in a direction away from it, and an arc-shaped eccentric-side curved surface 17c that continues to the apex 17a.

In the present embodiment, since a pair of top portions 17a is provided, a pair of top side curved surfaces 17b are provided at symmetrical positions with the axis O interposed therebetween.
Here, the radius of curvature of the top-side curved surface 17b is preferably as large as possible in order to keep the moment of inertia of the cross section of the intermediate shaft portion 17 large.

  The eccentric-side curved surface 17c smoothly continues to the top-side curved surface 17b with no corners in front of the top portion 17a in the rotational direction. And the eccentric side curved surface 17c is provided in the position containing the intersection P of the virtual line X extended in said eccentric direction, and the outer edge of one area | region AR, and is extended on the outer edge along the outer edge.

In the present embodiment, since a pair of top portions 17a is provided, a pair of eccentric-side curved surfaces 17c at symmetrical positions with respect to the axis O are provided. Thereby, one eccentric side curved surface 17c extends along the outer edge of one area AR continuously from one top portion 17a to one top side curved surface 17b extending forward in the rotational direction R, while the other side Is connected to the top portion 17a. The other eccentric-side curved surface 17c is continuous with the other top-side curved surface 17b extending forward from the other top portion 17a in the rotational direction R in the rotational direction R, and extends along the outer edge of the one area AR. 17a.
In other words, the intermediate shaft portion 17 is formed by the top-side curved surface 17b, and the intermediate shaft portion 17 is substantially elliptical, rugby ball-shaped, or almond-shaped, and a part of the front portion in the rotational direction of the top portion 17a is partly radially inward. It has a shape that is scraped away.
Here, when processing the top side curved surface 17b, in order to perform processing while suppressing the amount of cutting, for example, the center of the processing circle is arranged on the rear side in the rotation direction R of the rotary shaft 15 with respect to the virtual line Y, It is possible to cut the intermediate shaft portion 17 in an arc shape. Further, the angle δ from the imaginary line Y to the connection point between the top side curved surface 17b and the top side curved surface 17b and the eccentric side curved surface 17c continuing forward in the rotation direction R is larger than the angle α. (Α <δ) and δ are preferably as close to α as possible.

Here, the value of the angle α is, for example, a value larger than 0 degree and smaller than 5 degrees in the present embodiment.
As shown in FIGS. 4A and 4B and Table 1, in any condition (HP (discharge side pressure) / LP (suction side pressure)), the intermediate shaft portion 17 has an eccentric direction. It has been confirmed from experimental results that the maximum gas load acts in the range of more than 5 degrees and less than 41 degrees toward the rear of the rotation direction R with reference to an imaginary line Y extending in a direction perpendicular to the rotation direction R. That is, the range in which the maximum gas load acts is a range of α = 5 degrees to 41 degrees.

また表１におけるＨＰ／ＬＰの値は、一般的な空調機でのＨＰ／ＬＰを想定して設定した。

The HP / LP values in Table 1 were set assuming HP / LP in a general air conditioner.

  According to the rotary compressor 1 of the present embodiment described above, an angle larger than 0 degree and smaller than 5 degrees on the rear side in the rotation direction R with respect to the direction in which the top part 17a of the intermediate shaft part 17 is orthogonal to the eccentric direction. It is arranged at a position shifted by. That is, the top portion 17a is not arranged on the virtual line Y extending in the direction orthogonal to the eccentric direction.

  Therefore, since the diameter of the intermediate shaft portion is the largest at the position where the top portion 17a is provided, the cross-sectional secondary moment of the intermediate shaft portion can be increased at this position, and the rigidity of the intermediate shaft portion can be improved. Therefore, even when a compression load is applied to each of the piston rotors 14A and 14B, it is possible to suppress the bending deformation of the rotating shaft 15.

  In particular, the maximum load during compression is in the range of 5 degrees or more and 41 degrees or less on the rear side in the rotation direction R with respect to the intermediate shaft portion 17 as shown in FIGS. 4A and 4B and Table 1 above. The knowledge that it acts was obtained. Therefore, the maximum load at the time of compression does not act on the front side in the rotation direction R from the top portion 17a.

In this regard, in this embodiment, the top portion 17a is disposed at a position shifted by an angle α larger than 0 degree and smaller than 5 degrees on the rear side in the rotation direction R with respect to the direction orthogonal to the eccentric direction. Further, the thickness of the intermediate shaft portion 17 on the front side in the rotation direction R is thinner than the columnar shape.
However, in the portion where the thickness of the intermediate shaft portion 17 is thin, the load acting at the time of compression is smaller than the maximum load as described above, so even if the top portion 17a is provided at the above position, the intermediate shaft The strength of the portion 17 can be sufficiently secured. And the weight reduction of the intermediate shaft part 17 can also be achieved.

  In the present embodiment, the outer peripheral surface of the intermediate shaft portion 17 is disposed in one area AR in which the outer peripheral edge of the main shaft piston rotor 14A and the outer peripheral edge of the auxiliary shaft piston rotor 14B overlap. The top portion 17a is formed so as to be scraped off at the front side in the rotation direction R of the top portion 17a. For this reason, when the rotating shaft 15 rotates, the lubricating oil existing around the intermediate shaft portion 17 is smoothly guided toward the top portion 17a of the intermediate shaft portion 17, and the intermediate shaft portion is directed rearward in the rotation direction R. The outer peripheral surface of 17 is smoothly distributed. Accordingly, it is possible to reduce a stirring loss when the lubricating oil is stirred by the intermediate shaft portion 17 during rotation.

  In particular, in the present embodiment, by providing the top side curved surface 17b and the eccentric side curved surface 17c as the outer peripheral surface of the intermediate shaft portion 17, the intersection point is formed on the outer peripheral surface of the intermediate shaft portion 17 on the front side in the rotation direction R from the top portion 17a. A smooth curved surface without corners is formed from P toward the top portion 17a. Therefore, when the lubricating oil is agitated by the rotating shaft 15, the lubricating oil is smoothly guided through these surfaces from the eccentric curved surface 17c toward the top curved surface 17b. Accordingly, even the intermediate shaft portion 17 having the top portion 17a can reduce the stirring loss of the lubricating oil.

  Furthermore, by providing a pair of top portions 17a at symmetrical positions across the axis O, the lubricating oil is smoothly guided on the outer peripheral surface of the intermediate shaft portion 17 while ensuring the strength of the intermediate shaft portion 17, and the stirring loss of the lubricating oil is reduced. Can be further reduced. Further, during rotation, the centrifugal force acting on the position of the top portion 17a of the intermediate shaft portion 17 is canceled out by the top portions 17a, and the stability during rotation of the rotary shaft 15 can be improved.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations of the embodiments in the embodiments are examples, and the addition and omission of configurations are within the scope not departing from the gist of the present invention. , Substitutions, and other changes are possible. Further, the present invention is not limited by the embodiments, and is limited only by the scope of the claims.
For example, as shown in FIG. 5, the top portion 17a may be provided only in one place. The apex portion 17a is disposed behind the imaginary line Y orthogonal to the eccentric direction at a position shifted by an angle β larger than 0 degree and smaller than 5 degrees behind the rotation direction R.

  Further, as shown in FIG. 6, a pair of top portions 17a are provided, and the positions at which the top portions 17a are arranged are at angles θ1, θ2 behind the rotation direction R with respect to a virtual line Y orthogonal to the eccentric direction. It is arranged at a shifted position. θ1 and θ2 are angles different from each other, and both are angles larger than 0 degree and smaller than 5 degrees behind the rotation direction R with respect to the virtual line Y orthogonal to the eccentric direction.

  Further, the top side curved surface 17b of the intermediate shaft portion 17 is not limited to an arcuate curved surface, and may be formed in a planar shape, for example.

  Moreover, the top part 17a may be arrange | positioned outside the one area | region AR.

  The angles α, β, θ1, and θ2 are set to values larger than 0 degree and smaller than 5 degrees as an example, but are not limited thereto. That is, it is only necessary that the apex portion 17a having the largest distance from the axis O be located at the position where the maximum load is applied to the intermediate shaft portion 17, and the values of α, β, θ1, and θ2 are larger than 0 degree and smaller than 45 degrees. It only has to be. In particular, when the top portion 17a is disposed outside the one area AR, the diameter of the intermediate shaft portion 17 is not extremely reduced behind the rotation direction R of the top portion 17a. α, β, θ1, and θ2 need not be limited to values larger than 0 degrees and smaller than 5 degrees as described above.

DESCRIPTION OF SYMBOLS 1 ... Rotary compressor 10 ... Partition plate 11 ... Casing 12A ... Main shaft side cylinder 12B ... Sub shaft side cylinder 12S1, 12S2 ... Cylinder inner wall surface 13A ... Main shaft side eccentric shaft part 13B ... Sub shaft side eccentric shaft part 13Aa, 13Ba ... Out Peripheral edge 14A ... Main shaft piston rotor 14B ... Sub-shaft piston rotors 14Aa, 14Ba ... Outer peripheral edge 15 ... Rotating shaft 16 ... Shaft body 18 ... Drive portion 17 ... Intermediate shaft portion 17a ... Top portion 17b ... Top side curved surface 17c ... Eccentric side curved surface 19 ... Rotor 20 ... Stator 22A ... Opening 22B ... Opening 23A ... Suction port 23B ... Suction port 24 ... Accumulator 24a ... Suction port 25 ... Stay 26A ... Suction pipe 26B ... Suction pipe 27 ... Discharge port S ... Compression chamber S1 ... First compression chamber S2 ... second compression chamber R ... rotational direction O ... axis O1 ... eccentric shaft O2 ... eccentric shaft AR ... one region X ... virtual line P ... intersection

Claims (6)

A rotary shaft of a rotary compressor that is rotatably supported with respect to a casing having a compression chamber on the inside, and is capable of compressing fluid together with lubricating oil by being driven to rotate about an axis,
A shaft body extending in a rod shape around the axis;
A spindle piston rotor that is eccentrically provided in the shaft body and is accommodated in a first compression chamber of the compression chambers;
The main shaft piston rotor and the main shaft piston rotor are arranged away from each other in the direction of the axis, and are eccentric with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. A countershaft piston rotor to be accommodated;
An intermediate shaft provided in the shaft main body at a position sandwiched between the main shaft piston rotor and the sub shaft piston rotor;
The intermediate shaft portion, when viewed in a cross section perpendicular to the axis, is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor, and the outer peripheral surface of the intermediate shaft portion and the axis On the outer peripheral surface having the largest distance of
A pair of the top portions are provided at symmetrical positions across the axis,
When the intermediate shaft portion is viewed in a cross section perpendicular to the axis, the intermediate shaft portion rotates from the region where the outer peripheral edge of the main shaft piston rotor and the outer peripheral edge of the sub-axis piston rotor overlap. Only the portion on the front side in the direction is partially cut away toward the inner side in the radial direction, so that the top portion is perpendicular to the eccentric direction and passes through the axis. And a rotary shaft of the rotary compressor disposed at a position shifted at an angle larger than 0 degree and smaller than 45 degrees on the rear side in the rotation direction.   The outer peripheral surface of the intermediate shaft portion is disposed in a region where the outer peripheral edge of the main shaft piston rotor and the outer peripheral edge of the sub-shaft piston rotor overlap when viewed in a cross section perpendicular to the axis. A rotary shaft of the rotary compressor according to 1. A rotary shaft of a rotary compressor that is rotatably supported with respect to a casing having a compression chamber on the inside, and is capable of compressing fluid together with lubricating oil by being driven to rotate about an axis,
A shaft body extending in a rod shape around the axis;
A spindle piston rotor that is eccentrically provided in the shaft body and is accommodated in a first compression chamber of the compression chambers;
The main shaft piston rotor and the main shaft piston rotor are arranged away from each other in the direction of the axis, and are eccentric with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. A countershaft piston rotor to be accommodated;
An intermediate shaft portion provided in the shaft main body at a position where the lubricating oil is present around and sandwiched between the main shaft piston rotor and the sub shaft piston rotor;
With
The intermediate shaft portion, when viewed in a cross section perpendicular to the axis, is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor, and the outer peripheral surface of the intermediate shaft portion and the axis On the outer peripheral surface having the largest distance of
When viewed in a cross section perpendicular to the axis, the outer peripheral surface of the intermediate shaft portion is disposed in a region where the outer peripheral edge of the main shaft piston rotor and the outer peripheral edge of the sub-shaft piston rotor overlap.
Said top portion, the rotational direction of Carlo Tari compressor rearward are disposed in a position displaced at an angle smaller than the larger 5 degrees above 0 degrees with respect to a virtual line passing through the axis and perpendicular to the eccentric direction Axis of rotation. The outer peripheral surface of the intermediate shaft portion, and a top side curved surface extending convexly curved in a direction away from the axis toward the front of the rotational direction the arranged inside the outer edge of a region from the top portion,
An eccentric curved surface that extends smoothly along the outer edge of the one region and is provided at a position that includes an intersection of an imaginary line that extends in the eccentric direction and the outer edge of the one region, and that is smoothly continuous with the top-side curved surface. Item 4. The rotary shaft of the rotary compressor according to Item 2 or 3. A rotary shaft of a rotary compressor that is rotatably supported with respect to a casing having a compression chamber on the inside, and is capable of compressing fluid together with lubricating oil by being driven to rotate about an axis,
A shaft body extending in a rod shape around the axis;
A spindle piston rotor that is eccentrically provided in the shaft body and is accommodated in a first compression chamber of the compression chambers;
The main shaft piston rotor and the main shaft piston rotor are arranged away from each other in the direction of the axis, and are eccentric with respect to the main shaft body in a direction different in phase by 180 degrees from the main shaft piston rotor. A countershaft piston rotor to be accommodated;
An intermediate shaft portion provided in the shaft main body at a position where the lubricating oil is present around and sandwiched between the main shaft piston rotor and the sub shaft piston rotor;
With
The intermediate shaft portion, when viewed in a cross section perpendicular to the axis, is convex in a direction intersecting the eccentric direction of the main shaft piston rotor and the sub shaft piston rotor, and the outer peripheral surface of the intermediate shaft portion and the axis On the outer peripheral surface having the largest distance of
The top portion is disposed at a position shifted by an angle larger than 0 degree and smaller than 45 degrees on the rear side in the rotation direction with respect to a virtual line passing through the axis perpendicular to the eccentric direction,
A pair of the top portions are provided at symmetrical positions across the axis,
In each of the pair of the top, the rotation direction of the rotation axis of Carlo Tari compressor displacement amount of the angle of the rear side different from each other with respect to a direction perpendicular to the eccentric direction. The rotating shaft according to any one of claims 1 to 5,
A drive unit that rotationally drives the rotary shaft;
A casing that houses the rotating shaft and the drive unit, and that has the first compression chamber and the second compression chamber inside,
A rotary compressor.

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