JP2013167210A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To efficiently suppress generation of noise.SOLUTION: A rotor 37 constituting a motor 36 of a compressor 10 is cylindrical. A shaft 23 is inserted through a hole 51 formed at a central part of the rotor. A guide groove 50 is formed in the shaft 23 continuously in an axial direction thereof. A guide projection 52 is formed on an inner circumferential surface of the hole 51 continuously along the axial direction of the shaft 23. The guide projection 52 can relatively slide and move in a direction in which the guide groove 50 continues, while being inserted into the guide groove 50. Accordingly, the rotor 37 can slide and move along the axial direction of the shaft 23.

Description

  The present invention relates to a rotary compressor used in a refrigeration apparatus.

As shown in FIG. 17, the rotary compressor used in the refrigeration apparatus includes a cylinder 2 having a cylindrical inner wall surface and a piston provided eccentrically with respect to the center of the cylinder 2 in a sealed container 1. And a rotor 3. The piston rotor 3 is provided on a shaft 4 provided along the central axis of the cylinder 2. The shaft 4 is rotatably provided around its axis via bearings 5A and 5B fixed to the cylinder 2. The shaft 4 is provided with a rotor 6 </ b> A constituting a motor 6 for rotating the shaft 4. A stator 6B fixed to the inner peripheral surface of the container 1 is disposed on the outer peripheral side of the rotor 6A. When the stator 6B is energized, the shaft 4 is rotationally driven, and the piston rotor 3 rotates in the cylinder 2. .
Then, the refrigerant is sucked into the compression chamber formed between the cylinder 2 and the piston rotor 3, and the volume of the compression chamber is reduced by the rotation of the piston rotor 3, and the refrigerant is compressed and discharged.

  During the operation of such a rotary compressor, a noise such as googling may occur. This is because the piston rotor 3 and the shaft 4 vibrate within the clearance of the bearings 5A and 5B supporting the shaft 4 due to pressure pulsation generated above and below the rotor 6A. The shaft 5 vibrates in the axial direction and interferes with the bearings 5A and 5B (particularly the lower bearing 5B), and noise is generated.

  On the other hand, a proposal has been made to reduce noise by reducing the clearance between the bearings 5A and 5B and the piston rotor 3 in the axial direction of the shaft 4 (see, for example, Patent Document 1).

Japanese Utility Model Publication No. 64-15792

  However, in order to reduce the above clearance, there is a problem that the processing cost increases.

On the other hand, the structure which offsets the magnetic center C1 of the rotor 6A which comprises the motor 6, and the magnetic center C2 of the stator 6B to the axial direction of the shaft 4 can be considered. As shown in FIG. 17, when the magnetic force center C1 of the rotor 6A is offset above the magnetic force center C2 of the stator 6B, the rotor 6A and the shaft 4 are attracted downward by the magnetic field generated by the stator 6B. 3 is pressed against the lower bearing 5B, thereby suppressing the generation of noise.
However, in such a configuration, since the friction between the piston rotor 3 and the lower bearing 5B is increased, the loss of the rotational driving force of the shaft 4 is increased, and the compression efficiency of the refrigerant is reduced.

On the other hand, the magnetic center C1 of the rotor 6A and the magnetic center C2 of the stator 6B are offset in the opposite direction to the above, and the rotor 6A and the shaft 4 are lifted upward by the magnetic field generated by the stator 6B. It is also conceivable to reduce the occurrence of noise by reducing the piston rotor 3 from contacting the lower bearing 5B.
However, in such a configuration, when the motor 6 rotates at high speed and field weakening control is performed, the magnetic field generated by the motor 6 is weakened, and the force to lift the rotor 6A and the shaft 4 upward is weakened. Falls and contacts the lower bearing 5B, and noise is generated.
The present invention has been made based on such a technical problem, and an object thereof is to provide a rotary compressor capable of effectively suppressing the generation of noise.

The rotary compressor of the present invention made for this purpose is rotatably supported by a cylinder in which a refrigerant is supplied inside and a bearing provided above and below the cylinder in a case forming an outer shell, A shaft that passes through the cylinder, a piston rotor that is eccentrically provided in a direction perpendicular to the central axis of the shaft, and is driven to rotate eccentrically with respect to the center of the cylinder in the cylinder, and the shaft rotates about the central axis A motor having a stator and a rotor to be driven, and the rotor and the shaft can be moved relative to each other along the axial direction of the shaft, and the rotor and the shaft can be rotated by a joint mechanism that transmits the rotation around the shaft axis Are connected.
The rotor and the shaft are provided by the joint mechanism so as to be relatively movable along the axial direction of the shaft, so that the rotor is held at a fixed position by the magnetic field generated by the stator during the operation of the motor, that is, the rotor In the floating state, the weight of the rotor does not act on the shaft. Therefore, even if the shaft is displaced in the axial direction and vibrations or the like are generated, the vibrations can be reduced as compared with the case where the rotor and the shaft vibrate integrally.

As such a joint mechanism, for example, a guide portion that is continuous in the axial direction of the shaft is formed on the outer peripheral surface of the shaft, and a slide portion that is slidable along the guide portion is formed on the rotor. Can be used.
Here, when the rotor is displaced in the axial direction of the shaft by the magnetic field generated by the stator, the shaft can be displaced together with the rotor by the slide portion abutting against one end of the guide portion. Thereby, a shaft can be made to float with a rotor, and generation | occurrence | production of the vibration by a shaft can also be suppressed.

The joint mechanism includes a shaft side coupling member provided at the end of the shaft and a rotor side coupling member provided at the end of the rotor and facing the shaft side coupling member. The ring member and the rotor side coupling member include a protrusion protruding from one side to the other, and a recess formed on the other side into which the protrusion is inserted, and the protrusion is connected to the shaft side coupling member in the recess. The rotor side coupling member can be used so as to be slidable in the direction of approaching and separating from each other.
In this case, it is possible to further include a bearing fixed to the case and rotatably supporting the rotor side coupling member. Thereby, rotation of a rotor side coupling member and a rotor can be supported stably.

  Furthermore, you may form the oil supply hole which supplies the lubricating oil contained in the refrigerant | coolant compressed with a rotary compressor to a joint mechanism in a shaft.

  ADVANTAGE OF THE INVENTION According to this invention, the vibration which arises when a shaft displaces to the axial direction can be reduced by providing a rotor and a shaft so that relative movement is possible along the axial direction of a shaft.

It is sectional drawing of the compressor in this Embodiment. It is a figure which shows the cylinder and piston rotor of a compressor, and is sectional drawing in the surface orthogonal to the axis line of a compressor. It is a figure which shows the structure of the rotor and shaft in 1st embodiment. It is a figure which shows the modification of 1st embodiment. It is a figure which shows the further modification of 1st embodiment. It is a figure which shows the structure of the rotor and shaft in 2nd embodiment, and a figure which shows a coupling mechanism. It is a figure which shows the modification of 2nd embodiment. It is a figure which shows the further modification of 2nd embodiment. It is a figure which shows the modification of the coupling mechanism used by 2nd embodiment. It is a figure which shows the application example which can be combined with 1st, 2nd embodiment. It is a figure which shows the modification of the application example shown in FIG. It is a figure which shows the modification of the application example shown in FIG. It is a figure which shows the further modification of the application example shown in FIG. It is a figure which shows the other example of an interference plate. It is a figure which shows the example which combined the bearing and rotor which support a rotor. It is a figure which shows the balance adjustment example of a piston rotor. It is sectional drawing which shows the structure of the conventional rotary compressor.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
[First embodiment]
FIG. 1 is a diagram showing a configuration of a rotary compressor 10 in the present embodiment.
As shown in FIG. 1, the compressor 10 has disk-like cylinders 20A and 20B provided in two upper and lower stages in a cylindrical sealed case 11 having a central axis in the vertical direction in FIG. The so-called two-cylinder type. Cylindrical cylinder inner wall surfaces 20S each having an axial line in the vertical direction are formed at the central portions of the cylinders 20A and 20B.

Cylindrical piston rotors 21A and 21B having an outer diameter smaller than the inner diameter of the cylinder inner wall surface 20S are disposed inside the cylinders 20A and 20B. Each of the piston rotors 21 </ b> A and 21 </ b> B is inserted and fixed to the eccentric shaft portions 40 </ b> A and 40 </ b> B of the shaft 23 along the center axis of the case 11. Thus, spaces R each having a crescent-shaped cross section are formed between the cylinder inner wall surfaces 20S of the cylinders 20A and 20B and the outer peripheral surfaces of the piston rotors 21A and 21B.
Here, the upper-stage piston rotor 21 </ b> A and the lower-stage piston rotor 21 </ b> B are provided so that their phases are different from each other.
A disk-shaped partition plate 24 is provided between the upper and lower cylinders 20A and 20B. The partition plate 24 partitions the space R in the upper cylinder 20A and the space R in the lower cylinder 20B into the compression chamber R1 and the compression chamber R2 without communicating with each other.

  As shown in FIG. 2, the upper and lower cylinders 20A and 20B are provided with blades 25 that divide the compression chambers R1 and R2 into two, respectively. In each of the cylinders 20A and 20B, the blade 25 is held in an insertion groove 26 formed to extend in the radial direction of the cylinders 20A and 20B so as to be able to advance and retract in a direction approaching and separating from the piston rotors 21A and 21B. Has been. The rear end portion 25a of the blade 25 is pressed by the coil spring 28, and the front end portion 25b is always pressed against the piston rotors 21A and 21B.

As shown in FIG. 1, the shaft 23 is supported by upper and lower bearings 29A and 29B fixed to upper and lower cylinders 20A and 20B by bolts so as to be rotatable around its axis.
The shaft 23 is formed with eccentric shaft portions 40A and 40B offset in the direction orthogonal to the central axis of the shaft 23 inside the piston rotors 21A and 21B. The eccentric shaft portions 40A and 40B have outer diameters slightly smaller than the inner diameters of the piston rotors 21A and 21B. Thereby, when the shaft 23 rotates, the eccentric shaft portions 40A and 40B rotate around the central axis of the shaft 23, and the upper and lower piston rotors 21A and 21B roll eccentrically in the cylinders 20A and 20B. At this time, since the blade 25 is pressed by the coil spring 28, the tip portion 25b advances and retreats following the movement of the piston rotors 21A and 21B, and is always pressed against the piston rotors 21A and 21B.

  The shaft 23 protrudes upward from the bearing 29 </ b> A, and a rotor 37 of a motor 36 for rotating the shaft 23 is provided at the protruding portion. A stator 38 is fixed to the inner peripheral surface of the case 11 so as to face the outer peripheral portion of the rotor 37.

  Openings 12A and 12B are formed on the sides of the case 11 at positions facing the outer peripheral surfaces of the cylinders 20A and 20B. The cylinders 20A and 20B are formed with suction ports 30A and 30B that communicate with the openings 12A and 12B up to a predetermined position on the cylinder inner wall surface 20S.

An accumulator 14 for gas-liquid separation of the refrigerant prior to supply to the compressor 10 is fixed to the case 11 via a stay 15 outside the case 11.
The accumulator 14 is provided with suction pipes 16A and 16B for letting the compressor 10 suck the refrigerant in the accumulator 14. The distal ends of the suction pipes 16A and 16B are connected to the suction ports 30A and 30B through the openings 12A and 12B.

In such a compressor 10, the refrigerant is taken into the accumulator 14 from the suction port 14 a of the accumulator 14, the refrigerant is separated into gas and liquid in the accumulator 14, and the gas phase is transferred from the suction pipes 16 </ b> A and 16 </ b> B to the cylinders 20 </ b> A and 20 </ b> B. Are supplied to the compression chambers R1 and R2, which are the internal spaces of the cylinders 20A and 20B, through the suction ports 30A and 30B.
Then, due to the eccentric rolling of the piston rotors 21A and 21B, the volumes of the compression chambers R1 and R2 are gradually reduced and the refrigerant is compressed. Discharge holes (not shown) for discharging the refrigerant are formed at predetermined positions of the cylinders 20A and 20B, and reed valves (not shown) are provided in the discharge holes. Thereby, when the pressure of the compressed refrigerant increases, the reed valve is pushed open, and the refrigerant is discharged to the outside of the cylinders 20A and 20B. The discharged refrigerant is discharged from a discharge pipe 42 provided at the top of the case 11 to an external pipe (not shown).

In the compressor 10 as described above, the shaft 23 is arranged in the axial direction of the shaft 23 within a clearance range of a predetermined dimension formed between the piston rotors 21A and 21B and the upper and lower bearings 29A and 29B. It is possible to slide along.
As shown in FIG. 3, a guide groove 50 that is continuous along the axial direction is formed on the outer peripheral surface of the shaft 23.
On the other hand, the rotor 37 has a cylindrical shape, and the shaft 23 is inserted through a hole 51 formed at the center thereof. A guide protrusion 52 that is continuous along the axial direction of the shaft 23 is formed on the inner peripheral surface of the hole 51. The guide protrusion 52 is relatively slidable in a direction in which the guide groove 50 continues in a state where the guide protrusion 52 is inserted into the guide groove 50. Thereby, the rotor 37 is slidable along the axial direction of the shaft 23.

  Further, as shown in FIG. 1, the rotor 37 has a built-in permanent magnet. When the rotor 37 is not rotating, the magnetic center C <b> 10 of the shaft 23 is relative to the magnetic center C <b> 20 of the stator 38. They are arranged offset downward along the axial direction.

In such a configuration, when the stator 38 is energized, the rotor 37 floats upward with respect to the stator 38 due to the magnetic field generated between the stator 38 and the rotor 37 (floating). At this time, when the rotor 37 floats, the guide protrusion 52 pushes up the upper end portion 50 a of the guide groove 50 from below, so that the shaft 23 floats together with the rotor 37.
As a result, the piston rotor 21B can be prevented from coming into contact with the lower bearing 29B, and the generation of noise can be suppressed.

  Here, when the motor 36 rotates at a high speed, an increase in the rotational speed can be secured by performing field-weakening control in which the phase of the current supplied to the stator 38 is advanced with respect to the induced voltage. In this case, since the magnetic field generated in the stator 38 is weakened, the rotor 37 stays at a position lower than the height at which the guide protrusion 52 hits the upper end portion 50a of the guide groove 50. In this state, the guide protrusion 52 of the rotor 37 floats at a position where it does not hit the lower end portion 50b of the guide groove 50 due to the magnetic field action of the permanent magnet. On the other hand, the shaft 23 is lowered and the piston rotor 21B comes into contact with the lower bearing 29. However, since the rotor 37 floats, the load of the rotor 37 does not act on the shaft 23. Thereby, when the compressor 10 is in a steady operation state, even if the piston rotor 21B comes into contact with the lower bearing 29B, only the dead weight of the shaft 23 acts, so the piston rotor 21B and the bearing 29B Noise generation at the time of a collision can be suppressed.

In addition, since the contact load between the piston rotor 21B and the bearing 29B is reduced as described above, the friction loss is reduced and the operating efficiency of the compressor 10 is increased.
In addition, conventionally, the rotor and the shaft are shrink-fitted and integrated, but due to the shrink-fitting accuracy, the axial position of the rotor and the shaft varies, but as described above, the axis of the shaft 23 By providing the rotor 37 so as to be slidable in the direction, it is freed from the problem of variations in the axial position of the shaft 23 and the rotor 37.

(Multiple modifications of the first embodiment)
Note that the following configuration can be combined with the configuration shown in the first embodiment.
For example, as shown in FIGS. 4A and 4B, a lubricating oil hole 55 that is continuous in the axial direction is formed at the center of the shaft 23, and the guide groove 50 is continuous with the lubricating oil hole 55. A plurality of oil supply holes 56 are formed along the length direction of the guide groove 50.
According to such a configuration, with the rotation of the shaft 23, the refrigerant containing the lubricating oil in the compression chamber is sucked up from the lower end portion of the lubricating oil hole 55 on the same principle as the centrifugal pump, and the oil supply hole 56. To the guide groove 50. Thereby, the space between the guide groove 50 and the guide protrusion 52 is lubricated, the sliding resistance is reduced, and the movement of the shaft 23 and the rotor 37 can be performed independently and smoothly. Therefore, even when the magnetic field is weakened and the rotor 37 is lowered, the shaft 23 is less likely to follow this, and the generation of noise can be suppressed.

  Further, in addition to the configuration shown in FIG. 4, as shown in FIG. 5A, a lubricating oil groove 57 that is continuous in the direction from the center portion of the shaft 23 toward the outer peripheral portion is formed on the side surface of the guide groove 50. May be. As a result, the lubricating oil discharged into the guide groove 50 from the oil supply hole 56 flows toward the outer peripheral side through the lubricating oil groove 57 due to the centrifugal force of the shaft 23, and between the guide groove 50 and the guide protrusion 52. Lubricity is further increased.

Further, as shown in FIG. 5 (b), a lubricating oil hole 58 continuous in the axial direction of the shaft 23 is formed at a position offset from the center of the shaft 23, and the guide groove is continuous with the lubricating oil hole 58. You may form the oil supply hole 59 opened to 50 side 50d.
Even in such a configuration, the lubricating oil sucked up by the lubricating oil hole 58 can be supplied between the guide groove 50 and the guide protrusion 52 from the oil supply hole 59, and the lubricity thereof can be improved.

[Second Embodiment]
Next, 2nd embodiment of the rotary compressor concerning this invention is shown. In the second embodiment described below, the difference from the first embodiment is only a part of the configuration, and the overall configuration of the other compressor 10 is the same as that of the first embodiment. is there. Therefore, in the following, the description will be focused on the configuration different from that of the first embodiment, and the same reference numerals will be given to the configuration common to the first embodiment, and the description thereof will be omitted.
In the first embodiment, the shaft 23 is configured to penetrate the central portion of the cylindrical rotor 37. However, in the compressor 10 according to the present embodiment, as shown in FIG. The upper end portion of the shaft 61 is connected to the rotor 62 via the coupling mechanism 63 without passing through the rotor 62.

  The coupling mechanism 63 includes a lower coupling member 64 and an upper coupling member 65 that face each other along the axial direction of the shaft 61. As shown in FIGS. 6 (a) and 6 (b), the lower coupling member 64 and the upper coupling member 65 are respectively made of disc-shaped bases 64a and 65a and protrusions 64b and 65b protruding on the bases 64a and 65a. It consists of. The lower coupling member 64 and the upper coupling member 65 are formed so that the bases 64a and 65a face each other, and the protrusions 64b and 65b are formed between the counterpart protrusions 64b and 64b and the recess 64c formed between 65b and 65b. , 65c are engaged with each other in a state in which displacement in the circumferential direction is restricted and displacement in a direction approaching and separating from each other is allowed.

As a result, the rotor 62 can be displaced in the vertical direction with respect to the shaft 61 while restraining displacement in the circumferential direction. In such a configuration, only the rotor 62 moves up and down by the magnetic field generated in the stator 38 when the compressor 10 is operated. For this reason, there is no need to form a clearance for moving the shaft 61 up and down between the piston rotors 21A and 21B and the upper and lower bearings 29A and 29B. Can be suppressed.
When the compressor 10 is started, the rotor 62 maintains the floated state by the magnetic field generated in the stator 38 and the magnetic field generated by the permanent magnet provided in the rotor 62, so that generation of noise during operation can be suppressed.
When the compressor 10 is started and stopped, the collision noise between the upper coupling member 65 and the lower coupling member 64 that descends with the rotor 62 when the magnetic field generated in the stator 38 is turned ON / OFF is suppressed. As shown in FIG. 6B, it is preferable to sandwich a buffer member 66 made of a rubber-based material or a resin-based material between the upper coupling member 65 and the lower coupling member 64.

  Moreover, according to the above structure, since it is not necessary to make the shaft 61 penetrate the rotor 62, the rotor 62 can also be made into a solid structure. Thereby, the diameter of the rotor 62 can be reduced, its own weight can be reduced, and the vibration propagation in the vertical direction to the shaft 61 side can be further suppressed. In addition, if the diameter of the rotor 62 is reduced, the performance and size of the compressor 10 can be improved by improving the efficiency and size of the motor 36.

  The coupling mechanism 63 may be a commercially available one, and even if manufactured, the structure is simple and the manufacturing can be easily performed as compared with the shaft 23 having the guide groove 50.

Conventionally, in the structure in which the shaft and the rotor are shrink-fitted, the rotation balance is achieved by integrating them, and the processing / manufacturing difficulty is high. However, according to the configuration of this embodiment, the coupling Since the shaft 61 and the rotor 62 are independent of each other as a rotating body by the mechanism 63, it is possible to perform a balance design with the shaft 61 alone.
In the two-cylinder compressor 10 including two cylinders 20A and 20B and piston rotors 21A and 21B shown in FIG. 1, one piston rotor 21A and the other piston rotor 21B provided integrally with a shaft 61 are provided. However, when the configuration of the present embodiment is applied to a one-cylinder compressor including a pair of cylinders and a piston rotor 21A, a hole 90 is formed in the piston rotor 21A as shown in FIG. Alternatively, the shaft 61 can be balanced by offsetting the oil supply holes 67 formed in the shaft 61 as described later.

  In the second embodiment, the shaft 61 and the lower coupling member 64, and the rotor 62 and the upper coupling member 65 may be integrated.

  Further, as shown in FIG. 7, an oil supply hole 67 that penetrates the shaft 61 and the lower coupling member 64 is formed, and lubrication between the lower coupling member 64 and the upper coupling member 65 is performed through the oil supply hole 67. You can also plan. Thereby, the operativity of the upper coupling member 65 and the rotor 62 can be improved, and the above effect can be made more remarkable.

(Modification of the second embodiment)
As shown in FIG. 8A, the upper coupling member 65 may be rotatably supported by a radial bearing 68 whose outer peripheral portion is fixed to the case 11 of the compressor 10 by welding or press fitting.
According to such a configuration, the clearance between the lower coupling member 64 and the upper coupling member 65 does not cause the rotational operations of the upper coupling member 65 and the rotor 62 to become unstable, and stabilizes them. Can be operated. Thereby, vibration in the radial direction of the upper coupling member 65 and the rotor 62 is suppressed, and the electromagnetic noise of the motor 36 can be reduced.
In addition, even when the rotor 62 falls unexpectedly, the rotor 62 can be received by the upper surface of the radial bearing 68, and the downward displacement of the rotor 62 can be restricted.

Further, as shown in FIG. 8B, the upper coupling member 65 may be rotatably supported by a thrust bearing 69 whose outer peripheral portion is fixed to the case 11 of the compressor 10 by welding or press fitting. it can.
According to such a configuration, the upper coupling member 65 and the rotor 62 can be stably rotated on the thrust bearing 69. Thereby, sliding friction during rotation of the rotor 62 can be remarkably reduced, and the performance of the motor 36 and the compressor 10 is improved.
In addition, since a clearance (relief) is provided between the lower coupling member 64 and the upper coupling member 65, there is room for the rotor 62 integrated with the upper coupling 65 to move in the up-down direction at this escape portion. There is. Therefore, as described above, if an offset is provided between the rotor 62 and the stator 38, the rotor 62 can be floated. At this time, the upper coupling 65 is not fixed to the thrust bearing. Therefore, since the thrust bearing 69 in this case only serves as a tray when the upper coupling 65 falls, a smooth bearing surface is sufficient.
On the other hand, it is more stable to fix the upper coupling 65 to the thrust bearing 69. However, if this form is adopted, the rotor 62 cannot float. At this time, as the thrust bearing 69, it is preferable to use a bearing provided with rolling elements such as rollers so that friction is reduced as much as possible.

Further, as shown in FIGS. 9A and 9B, as the coupling mechanism 63, a slider 72 is sandwiched between the upper hub 70 and the lower hub 71, and the upper hub 70 and the slider 72, and the slider 72 and the lower portion are sandwiched. The hub 71 may also have a so-called Oldham shape that extends in the radial direction of the shaft 61 and meshes with the ridges 73 and 74 and the grooves 75 and 76 that extend in directions orthogonal to each other.
Also in such a coupling mechanism 63, the shaft 61 and the rotor 62 can be movably coupled in the vertical direction along the axis of the shaft 61 while being restricted in the rotational direction. Such a coupling mechanism 63 is easy to manufacture, and the above-described effects can be obtained at a lower cost.

Further, as the coupling mechanism 63, as shown in FIG. 9 (c), an upper hub 77 and a lower hub 78 connected by a bellows-like metallic bellows 79 can be used. According to such a configuration, when the bellows 79 expands and contracts, the upper hub 77 and the lower hub 78 can move toward and away from each other, while the upper hub 77 and the lower hub 78 are restrained in the rotational direction.
Also in such a coupling mechanism 63, the shaft 61 and the rotor 62 can be movably coupled in the vertical direction along the axis of the shaft 61 while being restricted in the rotational direction. In particular, since no backlash occurs in the rotational direction between the upper hub 77 and the lower hub 78, the rotational force between the shaft 61 and the rotor 62 can be transmitted smoothly.

(Other application examples)
The following configurations can be combined with the configurations shown in the first and second embodiments.
That is, as shown in FIG. 10A, in the upper and lower spaces A1 and A2 of the motor 36 of the compressor 10, the primary component of the vibration generated when the motor 36 rotates depends on the dimensions of the space A1 and A2. May resonate with the natural frequency. When resonance occurs, pressure fluctuation due to vibration of the motor 36 is amplified, and as a result, the rotors 37 and 62 may be vibrated strongly in the vertical direction.
In order to prevent this, a disk-shaped interference plate 80 can be provided in the space A1 above the motor 36 or the space A2 below (in the example of FIG. 10A, the space A1 above). Thereby, the acoustic natural frequency of the space A1 or A2 is made higher than the primary component of vibration at the maximum rotational speed of the motor 36 (in the case of a one-cylinder compressor). In the two-cylinder compressor 10 having two cylinders 20A and 20B and piston rotors 21A and 21B, the acoustic natural frequency of the space A1 or A2 is determined from the secondary component of vibration at the maximum rotational speed of the motor 36. Also raise.

Such an interference plate 80 can be fixed to a bobbin (winding end) 38 a of the stator 38.
Further, as shown in FIGS. 10A and 10B, the interference plate 80 is formed with a through-hole 81 through which the coolant passes. The through hole 81 is preferably formed at a position separated from the refrigerant discharge pipe 42.

By providing the interference plate 80 described above, the vibration of the motor 36 can be further effectively reduced.
In addition, since the lubricating oil contained in the refrigerant is captured by the interference plate 80, the OC%, which is a percentage of the amount of oil in the refrigerant, can be reduced, and the discharge pipe 42 provided for reducing the OC% can be reduced. The insertion length into the case 11 can be shortened, and the cost can be reduced.

  As shown in FIG. 11, the interference plate 80 can also be formed in an umbrella shape so that the outer peripheral portion 80b is lower than the central portion 80a. As a result, the lubricating oil captured by the lower surface 80 c of the interference plate 80 flows to the outer peripheral side of the interference plate 80, and is easily returned to the lower portion of the compressor 10 along the inner peripheral surface of the case 11.

  In addition, as shown in FIG. 12, a hood 83 can be provided in the through hole 81 formed in the interference plate 80 to further capture the lubricating oil contained in the refrigerant passing through the through hole 81.

  Furthermore, as shown in FIG. 13, a hood 84 may be provided in the through hole 81 formed in the interference plate 80 so as to open in a direction along the rotation direction of the rotors 37 and 62. Such a hood 84 further captures the lubricating oil contained in the refrigerant passing through the through-hole 81, and sprays the refrigerant having passed toward the inner peripheral surface of the case 11. Then, since the specific gravity of the oil contained in a refrigerant | coolant is large, it is sprayed on the internal peripheral surface of case 11 with a centrifugal force, and can isolate | separate a refrigerant | coolant and oil more efficiently.

The interference plate 80 as described above may be fixed to the rotors 37 and 62 of the motor 36 as shown in FIG.
With such a configuration, the inertia at the time of rotation of the rotors 37 and 62 increases, whereby the rotation of the rotors 37 and 62 can be stabilized and torque fluctuation can be suppressed.

Further, as shown in FIG. 15, these interference plates 80 can also be constituted by radial bearings 88 that rotatably support the upper coupling member 65 shown in FIG. The outer peripheral portion of the radial bearing 88 is fixed to the inner peripheral surface of the case 11 by welding, press fitting, or the like.
According to such a configuration, the upper coupling member 65 and the rotor 62 can be operated stably. Thereby, vibration in the radial direction of the upper coupling member 65 and the rotor 62 is suppressed, and the electromagnetic noise of the motor 36 can be reduced.
In addition, since the radial bearing 88 also functions as the interference plate 80, it is possible to increase the separation efficiency between the refrigerant and the lubricating oil.

In the above-described embodiment, the configuration of the compressor 10 has been described. However, the configuration of each unit can be appropriately changed within a range that does not depart from the gist of the present invention.
In the above description, the two-cylinder compressor 10 including the two sets of cylinders 20A and 20B and the piston rotors 21A and 21B is taken as an example. However, the present invention is also applied to a compressor having one cylinder or three or more cylinders. it can.
In addition to this, as long as the gist of the present invention is not deviated, the configuration described in the above embodiment can be selected, changed to another configuration, or combined as appropriate.

DESCRIPTION OF SYMBOLS 10 Compressor 11 Case 20A, 20B Cylinder 21A, 21B Piston rotor 23, 61 Shaft 29A, 29B Bearing 36 Motor 37, 62 Rotor 38 Stator 50 Guide groove (guide part, joint mechanism)
50a Upper end 50b Lower end 52 Guide protrusion (slide part, joint mechanism)
63 Coupling mechanism (joint mechanism)
64 Lower coupling member (shaft side coupling member)
65 Upper coupling member (rotor side coupling member)
64b, 65b Protrusions 64c, 65c Recess 66 Buffer member 68, 88 Radial bearing 69 Thrust bearing 80 Interference plate

Claims (6)

In the case that forms the outer shell,
A cylinder to which refrigerant is supplied,
A shaft rotatably supported by bearings provided above and below the cylinder and penetrating through the cylinder;
A piston rotor that is eccentrically provided in a direction orthogonal to the central axis of the shaft, and is driven to rotate eccentrically with respect to the center of the cylinder in the cylinder;
A motor having a stator and a rotor for rotating the shaft around its central axis,
The rotor and the shaft are connected to each other by a joint mechanism that allows the rotor and the shaft to move relative to each other along the axial direction of the shaft and transmits rotation about the axis of the shaft to the rotor. Rotary compressor characterized by.   As the joint mechanism, a guide portion that is continuous in the axial direction of the shaft is formed on the outer peripheral surface of the shaft, and a slide portion that is slidable along the guide portion is formed on the rotor. The rotary compressor according to claim 1.   The shaft is displaced together with the rotor when the rotor is displaced in the axial direction of the shaft by the magnetic field generated by the stator, so that the slide portion hits one end of the guide portion. 2. The rotary compressor according to 2. As the joint mechanism, a shaft side coupling member provided at an end portion of the shaft, and a rotor side coupling member provided at an end portion of the rotor and opposed to the shaft side coupling member,
The shaft-side coupling member and the rotor-side coupling member include a protrusion that protrudes from one to the other, and a recess that is formed on the other and into which the protrusion is inserted, the protrusion being the recess 2. The rotary compressor according to claim 1, wherein the shaft side coupling member and the rotor side coupling member are slidable in a direction in which the shaft side coupling member and the rotor side coupling member approach and separate from each other.   The rotary compressor according to claim 4, further comprising a bearing fixed to the case and rotatably supporting the rotor-side coupling member.   6. The rotary according to claim 1, wherein an oil supply hole for supplying lubricating oil contained in a refrigerant compressed by the rotary compressor to the joint mechanism is formed in the shaft. Compressor.

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