JP2019183818A - Piston rotor, crank shaft, rotary compressor, and method for assembling crank shaft - Google Patents

Abstract

To suppress deterioration in performance of a compressor due to deflection.SOLUTION: A first piston rotor 13A is a piston rotor of a crank shaft 16 that rotates around an axial line O in a rotary compressor, and has a plurality of rotor divided bodies 131A having an annular shape centering on a center line. The plurality of rotor divided bodies 131A is movable relative to each other in a state where they are in contact with each other in a direction in which the center line extends.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a piston rotor, a crankshaft, a rotary compressor, and a method for assembling the crankshaft.

  For example, an apparatus including an accumulator and a compressor is known as an apparatus used for compressing a refrigerant in an air conditioner. The accumulator performs gas-liquid separation of the refrigerant prior to introduction into the compressor. The compressor and the accumulator are connected by a suction pipe. The compressor compresses only the gas-phase refrigerant supplied from the accumulator through the suction pipe to generate a high-pressure gas-phase refrigerant.

  For example, Patent Document 1 discloses a shaft (crankshaft), a roller (rotor) mounted on an eccentric part of the shaft, a cylinder having a cylinder chamber for accommodating the roller, and a front head that functions as a bearing at the end face of the cylinder. And a rear head. A plurality of grooves are formed on the roller.

JP 2010-223034 A

  Here, in the compressor as described above, the crankshaft may be bent by a gas load when the refrigerant is compressed, and the crankshaft may be inclined with respect to the rotor. As a result, the rotor may come into contact with the crankshaft. When such a piece contact occurs, the stress generated in the crankshaft partially increases to increase friction loss, which may impair the performance of the compressor or reduce reliability. Thus, there is an increasing demand for a compressor that can avoid the influence of bending of the crankshaft.

  The present invention has been made to solve the above-described problems, and provides a piston rotor, a crankshaft, a rotary compressor, and a method for assembling the crankshaft that can suppress a decrease in the performance of the compressor due to bending. The purpose is to do.

  According to the first aspect of the present invention, the piston rotor is a piston rotor of a crankshaft that rotates about an axis in a rotary compressor, and includes a plurality of annular rotor divided bodies, and the plurality of rotor divisions The bodies can be moved relative to each other in contact with each other.

  By setting it as such a structure, even if a crankshaft bends, the position of the radial direction of each rotor division body will shift so that the bending of a crankshaft may be followed. Thereby, the contact area of the piston rotor with respect to a crankshaft increases, and the influence per piece can be suppressed. As a result, the friction loss between the piston rotor and the crankshaft can be reduced. Therefore, reliability can also be improved.

  According to the second aspect of the present invention, the plurality of rotor divided bodies may have the same dimensions in the thickness direction.

  By setting it as such a structure, a piston rotor can be formed easily.

  According to a third aspect of the present invention, the crankshaft is provided on one side of the first shaft portion extending along the axis and the first shaft portion in the axial direction in which the axis extends, and has a diameter with respect to the axis. A first eccentric shaft portion that is eccentric in the direction and has a larger diameter than the first shaft portion, and extends along the axis, and is attached to one side of the first eccentric shaft portion in the axial direction. The piston rotor of the said aspect is arrange | positioned so that the said 1st eccentric shaft part may be covered from the outer side of the said radial direction.

  By adopting such a configuration, even if the crankshaft is bent and the first eccentric shaft portion is inclined, the radial position of each rotor divided body is adjusted so as to follow the inclination of the first eccentric shaft portion. Shift. Thereby, the contact area | region of the piston rotor with respect to a 1st eccentric shaft part increases, and the influence per piece can be suppressed. As a result, friction loss between the piston rotor and the first eccentric shaft portion can be reduced. Therefore, the reliability as a crankshaft can also be improved.

  According to the fourth aspect of the present invention, the crankshaft is provided on one side of the second shaft portion in the axial direction, is eccentric in a direction different from the first eccentric shaft portion, and the second shaft portion. A second eccentric shaft portion having a diameter larger than the shaft portion and smaller than the first eccentric shaft portion; an annular second piston rotor that covers the second eccentric shaft portion from outside in the radial direction; and the axis line And a third shaft portion attached to one side of the second eccentric shaft portion in the axial direction, wherein the second shaft portion and the third shaft portion are the first eccentric shaft. The first eccentric shaft portion is disposed so as to be partially recessed inward in the radial direction with respect to the first shaft portion, and the dimensions of the rotor divided bodies in the axial direction are smaller than the first shaft portion. Is smaller than the dimension of the second shaft portion in the axial direction. It may be.

  By adopting such a configuration, the axial center of the first eccentric shaft portion and the rotor can be moved by moving the rotor divided body from the third shaft portion side in the axial direction to the position of the second shaft portion in the radial direction. The axis of the divided body can be made coincident. That is, the plurality of rotor divided bodies can be smoothly fitted into the first eccentric shaft portion. Therefore, the dimension of the second shaft portion in the axial direction can be reduced regardless of the overall dimension of the first piston rotor in the axial direction. The crankshaft is most likely to bend at the second shaft portion with reference to the first shaft portion and the third shaft portion. By reducing the size of the second shaft portion, the bending can be effectively suppressed. Furthermore, since the second shaft portion is shortened, the overall dimension of the shaft body in the axial direction can be reduced. By these, the rigidity of a shaft main body becomes high and the possibility that a bending will arise can be reduced.

  According to the fifth aspect of the present invention, the rotary compressor accommodates the crankshaft of the above aspect and the first eccentric shaft portion, and a compression chamber is formed for compressing fluid as the crankshaft rotates. And a bearing portion that rotatably supports the first shaft portion.

  According to the sixth aspect of the present invention, a crankshaft assembling method is provided on a first shaft portion extending along an axis, and on one side of the first shaft portion in an axial direction in which the axis extends. A first eccentric shaft portion having a diameter larger than that of the first shaft portion, extending along the axis, and on one side of the first eccentric shaft portion in the axial direction. A first piston rotor having an attached second shaft portion, a plurality of rotor divided bodies that form an annular shape that covers the first eccentric shaft portion from the outside in the radial direction with respect to the axis, and the second shaft portion in the axial direction A second eccentric shaft portion that is eccentric in a direction different from the first eccentric shaft portion and has a larger diameter than the second shaft portion, and the second eccentric shaft portion is From the outside in the radial direction A crankshaft assembling method comprising: an annular second piston rotor; and a third shaft portion that extends along the axis and is attached to one side of the second eccentric shaft portion in the axial direction. And inserting the plurality of rotor divided bodies into the outer peripheral surface of the first eccentric shaft portion one by one from the third shaft side and bringing the plurality of rotor divided bodies into contact with each other in a state where they can move relative to each other. Including.

  ADVANTAGE OF THE INVENTION According to this invention, the fall of the performance of the compressor by bending can be suppressed.

It is sectional drawing which shows the structure of the compressor system which concerns on 1st embodiment of this invention. It is sectional drawing which shows the structure of the crankshaft which concerns on 1st embodiment of this invention. It is process drawing which shows the process of the assembly method of the crankshaft which concerns on 1st embodiment of this invention. It is explanatory drawing which shows the assembly method of the crankshaft which concerns on 1st embodiment of this invention. It is sectional drawing which shows the structure of the crankshaft which concerns on 2nd embodiment of this invention. It is explanatory drawing which shows the assembly method of the crankshaft which concerns on 2nd embodiment of this invention.

[First embodiment]
A first embodiment of the present invention will be described with reference to FIGS. Note that the expression “same” in the following description indicates substantially the same, and for example, tolerances in design and manufacturing errors are allowed.

  As shown in FIG. 1, the compressor system 100 according to the present embodiment includes an accumulator 24, suction pipes 26 </ b> A and 26 </ b> B (first suction pipe 26 </ b> A and second suction pipe 26 </ b> B), and the compressor 10. Yes. The compressor 10 according to the present embodiment is a two-cylinder type rotary compressor. The compressor 10 includes a motor 18 driven by an external power source, a compression mechanism unit 10A that compresses refrigerant (fluid) by being driven by the motor 18, and a housing 11 that covers the motor 18 and the compression mechanism unit 10A. I have.

  The compression mechanism 10A includes a crankshaft 16 rotated by a motor 18, piston rotors 13A and 13B (first piston rotor 13A and second piston rotor 13B) that rotate eccentrically as the crankshaft 16 rotates, and a piston rotor. Cylinders 12 </ b> A and 12 </ b> B (first cylinder 12 </ b> A and second cylinder 12 </ b> B) each having a compression chamber for accommodating 13 </ b> A and 13 </ b> B are provided.

  In the compression mechanism section 10A, a disk-shaped first cylinder 12A and a second cylinder 12B are provided in two upper and lower stages in a cylindrical housing 11. The housing 11 surrounds the first cylinder 12A and the second cylinder 12B to form a discharge space V in which the compressed refrigerant is discharged. Inside the first cylinder 12A and the second cylinder 12B, a cylindrical first piston rotor 13A and a second piston rotor 13B each having an outer shape smaller than the inside of the inner wall surface thereof are arranged. The first piston rotor 13A and the second piston rotor 13B are inserted and fixed to eccentric shaft portions 14A and 14B (first eccentric shaft portion 14A and second eccentric shaft portion 14B, which will be described later) of the crankshaft 16, respectively.

  The first piston rotor 13A of the upper cylinder 12A and the second piston rotor 13B on the lower stage are provided so that their phases are different from each other by 180 °. That is, the first piston rotor 13A is eccentric so that the position in the circumferential direction around the axis O is opposite to that of the second piston rotor 13B. A disk-shaped partition plate 15 is provided between the upper and lower first cylinders 12A and the second cylinder 12B. The partition plate 15 divides the space R in the upper cylinder 12 </ b> A and the lower space R into an upper compression chamber R <b> 1 and a lower compression chamber R <b> 2, respectively.

  The first cylinder 12A and the second cylinder 12B are fixed to the housing 11 by an upper bearing portion 17A and a lower bearing portion 17B. More specifically, the upper bearing portion 17A is fixed to the upper portion of the first cylinder 12A and has a disk shape. The outer peripheral surface of the upper bearing portion 17 </ b> A is fixed to the inner peripheral surface of the housing 11. The lower bearing portion 17B is fixed to the lower portion of the second cylinder 12B and has a disk shape. The outer peripheral surface of the lower bearing portion 17 </ b> B is fixed to the inner peripheral surface of the housing 11. That is, the first cylinder 12A and the second cylinder 12B are not directly fixed to the housing 11, but are fixed to the housing 11 via the upper bearing portion 17A and the lower bearing portion 17B.

  In the compressor 10, an accumulator 24 that gas-liquid separates the refrigerant prior to supply to the compressor 10 is fixed to the housing 11 via a stay 25. The accumulator 24 stores refrigerant before compression. Between the accumulator 24 and the compressor 10, a first suction pipe 26 </ b> A and a second suction pipe 26 </ b> B for allowing the compressor 10 to suck the refrigerant in the accumulator 24 are provided. One ends of the first suction pipe 26 </ b> A and the second suction pipe 26 </ b> B are connected to the lower part of the accumulator 24. The other ends of the first suction pipe 26A and the second suction pipe 26B pass through openings 22A and 22B, and suction ports 23A and 23B (first suction port 23A and second suction port) formed in the first cylinder 12A and the second cylinder 12B, respectively. Port 23B).

  Next, the configuration of the crankshaft 16 will be described in detail with reference to FIG. As shown in the figure, the crankshaft 16 extends along the axis O. The crankshaft 16 is supported rotatably around the axis O by an upper bearing portion 17A and a lower bearing portion 17B. The crankshaft 16 has a shaft body 16H, a first piston rotor 13A, and a second piston rotor 13B. The shaft body 16H includes a first shaft portion (main shaft) 16A, a first eccentric shaft portion (upper crankpin) 14A, a second shaft portion (intermediate shaft) 16B, and a second eccentric shaft portion (lower crankpin) 14B. And a third shaft portion (sub shaft) 16C.

  The first shaft portion 16A extends along the axis O. The first shaft portion 16A has the longest dimension in the axis O direction in the shaft body 16H.

  The first eccentric shaft portion 14A is integrally provided on one side (lower side) of the first shaft portion 16A in the axis O direction. The first eccentric shaft portion 14A is eccentric in the radial direction with respect to the axis O and has a disk shape having a larger diameter than the first shaft portion 16A. Accordingly, the portion of the outer peripheral surface of the first eccentric shaft portion 14A that coincides with the eccentric direction protrudes outward in the radial direction from the outer peripheral surface of the first shaft portion 16A. Moreover, the part (retreat part Ar) on the opposite side to the eccentric direction in the outer peripheral surface of the first eccentric shaft portion 14A is located on the inner side in the radial direction with respect to the axis O direction than the outer peripheral surface of the first shaft portion 16A. . That is, the first eccentric shaft portion 14A is formed so as to be recessed from the outer peripheral surface of the first shaft portion 16A in the retracted portion Ar. 14 A of 1st eccentric shaft parts are accommodated in the above-mentioned compression chamber R1. A first piston rotor 13A is attached to the first eccentric shaft portion 14A. The detailed configuration of the first piston rotor 13A will be described later.

  The second shaft portion 16B extends along the axis O and is integrally provided on one side of the first eccentric shaft portion 14A in the direction of the axis O. The second shaft portion 16B has a smaller diameter than the first shaft portion 16A. The second shaft portion 16B is disposed coaxially with the first shaft portion 16A. The dimension of the second shaft portion 16B in the axis O direction is smaller than any of the first shaft portion 16A, the first eccentric shaft portion 14A, the second eccentric shaft portion 14B, and the third shaft portion 16C.

  The second eccentric shaft portion 14B is integrally provided on one side of the second shaft portion 16B in the axis O direction. The second eccentric shaft portion 14B has a disk shape having a larger diameter than the second shaft portion 16B. The second eccentric shaft portion 14B protrudes radially outward from the outer peripheral surfaces of the second shaft portion 16B and the third shaft portion 16C over the entire circumference. An annular second piston rotor 13B that covers the second eccentric shaft portion 14B from the outside in the radial direction is attached to the outer peripheral surface of the second eccentric shaft portion 14B. The diameter of the second eccentric shaft portion 14B is the same as the diameter of the first eccentric shaft portion 14A. In addition, the outer diameter size of the second eccentric shaft portion 14B is not required to be larger than the diameter size of the first eccentric shaft portion 14A.

  The third shaft portion 16C extends along the axis O and is integrally attached to one side of the second eccentric shaft portion 14B in the direction of the axis O. The third shaft portion 16C is smaller than the first shaft portion 16A and has the same diameter as the second shaft portion 16B. The third shaft portion 16C is disposed coaxially with the first shaft portion 16A.

  The first shaft portion 16A protrudes upward (in the direction in which the motor 18 is located) from the upper bearing portion 17A. A rotor 19A of a motor 18 for rotating the crankshaft 16 is integrally provided at a portion protruding upward from the upper bearing portion 17A of the first shaft portion 16A. A stator 19B is fixed to the inner peripheral surface of the housing 11 so as to face the outer peripheral portion of the rotor 19A.

  The first piston rotor 13A is a piston rotor having a plurality (three in the present embodiment) of rotor divided bodies 131A that are in contact with each other in the axis O direction. The annular rotor divided bodies 131A are in contact with each other in the axis O direction. The dimensions (thickness dimensions) in the axis O direction of the rotor divided bodies 131A are the same and have the same shape. That is, the first piston rotor 13A is equally divided (three equal divisions) in the axis O direction. In other words, the dimension of the first eccentric shaft portion 14A in the axis O direction is the same as the dimension of the three rotor divided bodies 131A. Furthermore, the dimension in the axis O direction of one rotor divided body 131A is set to be equal to or smaller than the dimension of the second shaft portion 16B in the axis O direction. More specifically, the size of each rotor divided body 131A in the axis O direction is preferably slightly smaller than the dimension of the second shaft portion 16B in the axis O direction.

  Further, the retracted portion Ar of the first eccentric shaft portion 14A is located on the inner side in the radial direction with respect to the axis O direction than the outer peripheral surface of the first shaft portion 16A. As a result, of the three rotor divided bodies 131A, the rotor divided body 131A located on the other side in the axis O direction (that is, the uppermost side) is in contact with the end surface A1 of the first shaft portion 16A. Unlike the first piston rotor 13A, the second piston rotor 13B is formed as one member without being divided in the direction of the axis O. The dimension in the axis O direction of the second piston rotor 13B is equal to the dimension in the axis O direction of the second eccentric shaft portion 14B.

  Next, a method for assembling the crankshaft 16 according to this embodiment will be described with reference to FIGS. As shown in FIG. 3, the crankshaft assembly method includes a preparation step S1, a first rotor attachment step S2, and a second rotor attachment step S3.

  In the preparation step S1, the above-described shaft body 16H is prepared. In manufacturing the shaft body 16H, for example, the first shaft portion 16A, the first eccentric shaft portion 14A, the second shaft portion 16B, the second eccentric shaft portion 14B, and the third shaft portion 16C are sequentially welded in the axis O direction. The method and the method of cutting and forming all together are mentioned.

  Next, in the first rotor attachment step S2, the above-described first piston rotor 13A is attached to the first eccentric shaft portion 14A in the shaft body 16H.

  In attaching the first piston rotor 13A, the rotor divided bodies 131A are attached to the first eccentric shaft portion 14A one by one. That is, in this embodiment, since the first piston rotor 13A has the three rotor divided bodies 131A, the rotor divided body 131A is attached to the first eccentric shaft portion 14A in order three times.

  In attaching each rotor divided body 131A, as shown in FIG. 4, the rotor divided body 131A is inserted into the shaft body 16H from one side in the axis O direction. That is, the rotor divided body 131A is inserted from the third shaft portion 16C side.

  Next, the rotor divided body 131A is further moved upward (the other side in the direction of the axis O) and is allowed to pass through the second eccentric shaft portion 14B. Here, as described above, since the diameter dimension of the second eccentric shaft portion 14B is the same as the diameter size of the first eccentric shaft portion 14A, the rotor divided body 131A smoothly passes through the second eccentric shaft portion 14B. be able to.

  Furthermore, the rotor divided body 131A that has passed through the second eccentric shaft portion 14B is moved to the same position as the second shaft portion 16B in the axis O direction. Thereafter, the rotor divided body 131A is moved in a direction orthogonal to the axis O. Specifically, as shown in FIG. 4, the rotor divided body 131A is moved in the eccentric direction of the first eccentric shaft portion 14A, so that the axis center of the rotor divided body 131A and the axis center of the first eccentric shaft portion 14A are aligned. Is matched. From this state, the rotor divided body 131A is moved upward. The above steps are repeated for each of the plurality (three) of rotor divided bodies 131A. Thereafter, the plurality of rotor divided bodies 131A are in contact with each other in a state in which they can move relative to each other in the circumferential direction and the radial direction. Thereby, 1st rotor attachment process S2 is completed.

  Next, the second rotor attachment step S3 is performed. In the second rotor mounting step S3, the annular second piston rotor 13B formed as one member is fitted from the third shaft portion 16C side to the outer peripheral side of the second eccentric shaft portion 14B. As described above, all the processes related to the crankshaft assembling method according to the present embodiment are completed.

  Subsequently, the operation of the compressor system 100 according to the present embodiment will be described. In operating the compressor system 100, the motor 18 is first driven by the external power supply. As the motor 18 is driven, the shaft body 16H rotates around the axis O. As the shaft body 16H rotates, the first eccentric shaft portion 14A and the second eccentric shaft portion 14B rotate around the central axis (axis line O) of the shaft body 16H. The first piston rotor 13A and the second piston rotor 13B are eccentrically rotated in the compression chambers R1 and R2 so as to follow this turning. Due to the eccentric rotation of the first piston rotor 13A and the second piston rotor 13B, the volumes of the compression chambers R1, R2 change, and the refrigerant taken into the compression chambers R1, R2 is compressed. The compressed refrigerant is taken out through the discharge space V in the housing 11.

  Here, with the continuous operation of the compressor system 100, the shaft body 16H may bend. In particular, in the twin rotary compressor having the two first cylinders 12A and the second cylinder 12B as in the compressor system 100 according to the present embodiment, the shaft main body as compared with the single rotary compressor having only one cylinder. The length of 16H (dimension in the direction of the axis O) becomes longer. As a result, the shaft main body 16H is likely to be bent between the upper bearing portion 17A and the lower bearing portion 17B. When the shaft main body 16H is bent, the first eccentric shaft portion 14A formed near the center of the shaft main body 16H in the direction of the axis O is inclined, and the first piston rotor 13A is in a single-contact state with respect to the first eccentric shaft portion 14A. It may become. As a result, the stress generated in the first eccentric shaft portion 14A by the first piston rotor 13A partially increases, and the friction loss in the shaft body 16H may increase. Furthermore, there is a possibility of increasing noise and vibration.

  However, in the above configuration, the first piston rotor 13A is composed of a plurality of rotor divided bodies 131A that can move relative to each other while being in contact with each other in the direction of the axis O. That is, the first piston rotor 13A is divided into a plurality of parts in the axis O direction. Therefore, even if the shaft body 16H is bent and the first eccentric shaft portion 14A is inclined, the radial positions of the rotor divided bodies 131A are shifted so as to follow the inclination of the first eccentric shaft portion 14A. Thereby, the contact area | region of 13 A of 1st piston rotors with respect to 14 A of 1st eccentric shaft parts increases, and it can suppress the influence per piece. As a result, friction loss between the first piston rotor 13A and the first eccentric shaft portion 14A can be reduced. As a result, the performance of the compressor 10 due to the bending of the crankshaft 16 can be further improved. Moreover, the reliability as the crankshaft 16 and the reliability as the compressor 10 can be improved.

  Here, in attaching the first piston rotor 13A to the first eccentric shaft portion 14A, a step of inserting the annular first piston rotor 13A from the end in the axis O direction into the shaft main body 16H is taken. However, since the first eccentric shaft portion 14A is arranged so as to be partially recessed outward in the radial direction with respect to the first shaft portion 16A and the retreating portion Ar is formed, the first piston rotor 13A is moved along the axis O. The first shaft portion 16A in the direction cannot be inserted. Therefore, it is necessary to pass the first piston rotor 13A from the one side in the direction of the axis O in the order of the third shaft portion 16C and the second shaft portion 16B.

  At this time, for example, unlike the configuration of the above embodiment, when the first piston rotor is integrally formed and the dimension of the first piston rotor in the direction of the axis O is larger than the dimension of the second shaft portion 16B, Since the shaft portion 16B and the second eccentric shaft portion 14B are obstructed, the first piston rotor cannot reach the first eccentric shaft portion 14A and be attached accurately.

  However, in the configuration of the above embodiment, the plurality of rotor divided bodies 131A have the same dimensions in the axis O direction, and the dimensions in the axis O direction of each rotor divided body 131A are set to be equal to or smaller than the dimensions of the second shaft portion 16B. Has been. Therefore, by moving the rotor divided body 131A from the third shaft portion 16C side in the axis O direction to the position of the second shaft portion 16B and moving in the radial direction, the axis of the first eccentric shaft portion 14A and the rotor divided body are moved. The axial center of 131A can be made to coincide. That is, the plurality of rotor divided bodies 131A can be smoothly fitted into the first eccentric shaft portion 14A. For this reason, the plurality of rotor divided bodies 131A are independent of each other, so that the shaft main body 16H can be compared to the case where the first piston rotor is integrally formed or the rotor divided bodies 131A are partially connected. It is possible to improve the assemblability when attaching the first piston rotor 13A. Furthermore, the dimension of the second shaft portion 16B in the direction of the axis O can be reduced regardless of the overall dimensions of the first piston rotor 13A in the direction of the axis O. Thereby, the dimension of the shaft main body 16H in the direction of the axis O can be reduced as a whole. As a result, the rigidity of the shaft main body 16H is increased, and the possibility of occurrence of bending can be reduced. That is, according to the above configuration and assembly method, the compressor 10 with improved performance can be provided more simply.

  Further, the first piston rotor 13A can be easily formed by forming the first piston rotor 13A by the rotor divided body 131A having the same shape, not different shapes.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS. In addition, about the structure similar to said 1st embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted. As shown in FIG. 5, in the present embodiment, the second shaft portion 216 </ b> B of the crankshaft 216 includes a second shaft portion main body 40, a first reinforcement portion 41, and a second reinforcement portion 42.

  The second shaft main body 40 extends along the axis O and is integrally attached to one side of the first eccentric shaft 14A in the direction of the axis O. The second shaft portion main body 40 has a smaller diameter than the first shaft portion 16A. In the second shaft main body 40, the dimension in the axis O direction of the second shaft main body 40 arranged coaxially with the first shaft 16A is approximately the same as the dimension in the axis O direction of the third shaft 16C. Has been. That is, the second shaft portion main body 40 is formed to have a longer dimension in the axis O direction than the second shaft portion 16B of the first embodiment. In other words, the rotor divided body 131A is formed longer than the dimension in the axis O direction.

  The first reinforcing portion 41 is provided at a position where no gap is formed in the direction of the axis O with respect to the first eccentric shaft portion 14A. The first reinforcing portion 41 is eccentric in the same direction as the eccentric direction of the first eccentric shaft portion 14A. The first reinforcing portion 41 is integrally formed of the same material with respect to the second shaft portion main body 40 and the first eccentric shaft portion 14A. The end surface (compensation portion lower surface A1) on one side of the first reinforcing portion 41 in the axis O direction is spaced from the end surface (eccentric shaft portion upper surface A2) on the other side of the second eccentric shaft portion 14B in the axis O direction by a gap G1. Opposite. The dimension of the gap G1 in the axis O direction is slightly larger than the dimension of the rotor divided body 131A in the axis O direction.

  The 2nd reinforcement part 42 is provided in the position which does not open a clearance gap in the axis line O direction with respect to the 2nd eccentric shaft part 14B. The second reinforcing portion 42 is eccentric in the same direction as the eccentric direction of the second eccentric shaft portion 14B. That is, the second reinforcing portion 42 is eccentric in a direction opposite to the eccentric direction of the first eccentric shaft portion 14 </ b> A and the first reinforcing portion 41. The second reinforcing portion 42 is integrally formed of the same material with respect to the second shaft portion main body 40 and the second eccentric shaft portion 14B. The end surface (compensation portion upper surface A3) on the other side in the axis O direction of the second reinforcing portion 42 is spaced from the end surface (eccentric shaft portion lower surface A4) on the one side in the axis O direction of the first eccentric shaft portion 14A by a gap G2. Opposite. The dimension of the gap G2 in the direction of the axis O is slightly larger than the dimension of the rotor divided body 131A in the direction of the axis O.

  The first piston rotor 13A is attached to the crankshaft 216 having such a configuration through a process as shown in FIG. Specifically, as in the crankshaft assembly method described in the first embodiment, first, the rotor divided body 131A is inserted from the third shaft portion 16C side in the axis O direction and moved upward. When the rotor divided body 131A reaches the same position as the second reinforcing portion 42 in the axis O direction, the rotor divided body 131A is moved in a direction (radial direction) orthogonal to the axis O. Specifically, the rotor divided body 131A is moved in the same direction as the eccentric direction of the first reinforcing portion 41 and the first eccentric shaft portion 14A. From this state, the rotor divided body 131A is further moved upward. When the rotor divided body 131A reaches the same position as the first reinforcing portion 41 in the direction of the axis O, the rotor divided body 131A is further moved in the direction perpendicular to the axis O, and the axis of the rotor divided body 131A is The axial center of the first eccentric shaft portion 14A is matched. From this state, the rotor divided body 131A is further moved upward and fitted into the first eccentric shaft portion 14A. The first piston rotor 13A is attached to the crankshaft 216 by repeating this process for the number of rotor divided bodies 131A.

  According to said structure, the contact area of the 1st piston rotor 13A with respect to 14 A of 1st eccentric shaft parts increases by several rotor division bodies 131A similarly to 1st embodiment, and it can suppress the influence per piece. it can. As a result, friction loss between the first piston rotor 13A and the first eccentric shaft portion 14A can be reduced. As a result, the performance of the compressor 10 can be further improved.

  In addition, according to said structure, the 1st reinforcement part 41 and the 2nd reinforcement part 42 are provided in the 2nd axial part 216B. Thereby, the dimension of the radial direction of the 2nd axial part 216B is securable. As a result, the rigidity of the second shaft portion 216B as a whole is increased, and bending generated in the crankshaft 216 can be reduced.

  Here, the first reinforcing portion 41 and the second reinforcing portion 42 are each eccentric with respect to the axis O. Furthermore, the separation dimension in the axis O direction between the compensation section lower surface A1 and the eccentric shaft section upper surface A2 is slightly larger than the dimension in the axis O direction of the rotor divided body 131A. Further, the separation dimension in the direction of the axis O between the upper surface A3 of the compensation part and the lower surface A4 of the eccentric shaft part is slightly larger than the dimension in the direction of the axis O of the rotor divided body 131A. Therefore, as shown in FIG. 6, when attaching the rotor divided body 131A, the rotor divided body 131A can smoothly pass through the second eccentric shaft portion 14B. Therefore, by dividing the first piston rotor 13A into equal parts, the first shaft rotor 216B is not subjected to assembly restrictions, and the second shaft portion 216B is formed with a region having an enlarged radial dimension in order to ensure rigidity. A large dimension in the direction of the axis O of the piston rotor 13A can be secured. As a result, the compressor 10 with improved performance can be provided more simply.

(Other variations of the embodiment)
The embodiment of the present invention has been described in detail with reference to the drawings, but each configuration in the embodiment and combinations thereof are examples, and additions, omissions, and configurations of the configuration are within the scope 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, in the above embodiment, an example in which the second piston rotor 13B is integrally formed in the axis O direction has been described. However, it is also possible to adopt a configuration in which the second piston rotor 13B is divided in the direction of the axis O in the same manner as the first piston rotor 13A. According to this configuration, it is possible to further improve the performance of the compressor 10 by suppressing an increase in friction loss in the second piston rotor 13B.

  Further, the first piston rotor 13A is not limited to being formed by the rotor divided body 131A having the same shape as in the present embodiment. For example, the first piston rotor 13A may be configured by rotor divided bodies having different dimensions in the axis O direction.

DESCRIPTION OF SYMBOLS 100 ... Compressor system 10 ... Compressor 10A ... Compression mechanism part 11 ... Housing 12A ... First cylinder (cylinder)
12B ... Second cylinder (cylinder)
R1, R2 ... Compression chamber 13A ... First piston rotor (piston rotor)
13B ... Second piston rotor (piston rotor)
14A ... first eccentric shaft portion 14B ... second eccentric shaft portion 16 ... crankshaft 16A ... first shaft portion 16B, 216B ... second shaft portion 16C ... third shaft portion 17A ... Upper bearing portion 17B ... Lower bearing portion 18 ... Motor 19A ... Rotor 19B ... Stator 22A ... First opening (opening)
22B ... Second opening (opening)
23A ... First suction port (suction port)
23B ... Second suction port (suction port)
24 ... Accumulator 25 ... Stay 26A ... First suction pipe (suction pipe)
26B ... Second suction pipe (suction pipe)
131A ... rotor divided body 40 ... second shaft portion main body 41 ... first reinforcement portion 42 ... second reinforcement portion A1 ... compensation portion lower surface A2 ... eccentric shaft portion upper surface A3 ... -Compensation part upper surface A4 ... Eccentric shaft part lower surface Ar ... Retreat part G1, G2 ... Gap O ... Axis V ... Discharge space S1 ... Preparatory process S2 ... First rotor attachment Step S3 ... Third rotor attachment step

Claims (6)

A piston rotor of a crankshaft that rotates about an axis in a rotary compressor,
Having a plurality of rotor divided bodies in an annular shape,
The plurality of rotor divided bodies are piston rotors that can move relative to each other in contact with each other.   The piston rotor according to claim 1, wherein the plurality of rotor divided bodies have the same dimensions in the thickness direction. A first shaft portion extending along the axis;
A first eccentric shaft portion that is provided on one side of the first shaft portion in the axial direction in which the axis extends, is eccentric in the radial direction with respect to the axis, and has a larger diameter than the first shaft portion;
A second shaft portion extending along the axis and attached to one side of the first eccentric shaft portion in the axial direction;
The piston rotor according to claim 1 or 2, which covers the first eccentric shaft portion from the outside in the radial direction,
The piston rotor is a crankshaft disposed so as to cover the first eccentric shaft portion from the outside in the radial direction. Provided on one side of the second shaft portion in the axial direction, is eccentric in a direction different from the first eccentric shaft portion, and is larger than the second shaft portion and smaller than the first eccentric shaft portion. A second eccentric shaft portion having a radial dimension;
An annular second piston rotor that covers the second eccentric shaft portion from the outside in the radial direction;
A third shaft portion extending along the axis and attached to one side of the second eccentric shaft portion in the axial direction;
Further comprising
The second shaft portion and the third shaft portion have a smaller diameter than the first eccentric shaft portion,
The first eccentric shaft portion is disposed so as to be partially recessed inward in the radial direction with respect to the first shaft portion,
4. The crankshaft according to claim 3, wherein a dimension of each rotor divided body in the axial direction is equal to or smaller than a dimension of the second shaft portion in the axial direction. A crankshaft according to claim 3 or claim 4,
A compression mechanism portion that accommodates the first eccentric shaft portion and in which a compression chamber that compresses fluid in accordance with the rotation of the crankshaft is formed;
A bearing portion that rotatably supports the first shaft portion;
Rotary compressor equipped with. A first shaft portion extending along the axis;
A first eccentric shaft portion that is provided on one side of the first shaft portion in the axial direction in which the axis extends, is eccentric in the radial direction with respect to the axis, and has a larger diameter than the first shaft portion;
A second shaft portion extending along the axis and attached to one side of the first eccentric shaft portion in the axial direction;
A first piston rotor having a plurality of rotor divided bodies that form an annular shape that covers the first eccentric shaft portion from the outside in the radial direction with respect to the axis;
A second eccentric shaft portion that is provided on one side of the second shaft portion in the axial direction, is eccentric in a direction different from the first eccentric shaft portion, and has a larger diameter than the second shaft portion; ,
An annular second piston rotor that covers the second eccentric shaft portion from the outside in the radial direction;
A third shaft portion extending along the axis and attached to one side of the second eccentric shaft portion in the axial direction;
A crankshaft assembly method comprising:
Inserting the plurality of rotor divided bodies into the outer peripheral surface of the first eccentric shaft section one by one from the third shaft side, and bringing the plurality of rotor divided bodies into contact with each other while being relatively movable with respect to each other. Crankshaft assembly method.

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