JP6502078B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor having a rotary compressor and a motor applied to an air conditioner or the like.

  In a compressor used for an air conditioner, a compressor is driven by an electromagnetic motor. The electromagnetic motor includes a rotor, a stator, and the like, and the rotor and the compression unit are connected to each other via a drive shaft. The compressor rotates as the motor rotor rotates.

  One end side of the drive shaft is fixed on the compression unit side, and the other end side of the drive shaft is a free end on the rotor side. In the case of a rotary compressor, the drive shaft is provided with a crank pin (eccentric pin) on the compression unit side, and the crank pin is fitted to the roller of the compression unit. As a result, the center of gravity of the roller of the compression section is eccentric with respect to the axis of the drive shaft and is not located on the axis of the drive shaft. Therefore, in order to balance the centrifugal force generated by the rotation of the roller, balance weights, which are weights, are provided on the upper and lower surfaces of the rotor.

  In the following Patent Document 1, the center of the drive shaft is provided on the upper surface of the rotor with respect to the center of the rotor in order to suppress swinging of the rotor of the motor and reduce vibration and noise of the rotor during operation. Discloses a technique for displacing to the balance weight side of. Further, in Patent Document 2, in order to reduce vibration and noise during operation, the drive shaft has a first portion on which the rotor is mounted and a second portion on the cylinder chamber side, and the central axis of the first portion There is disclosed a technique for displacing the central axis of the second portion to the opposite side to the side on which the balance weight is installed.

Unexamined-Japanese-Patent No. 2006-200527 JP, 2009-74464, A

  During operation of the compressor, noise is generated by vibration due to bending inherent values of the drive shaft. The noise due to this resonance is greater than the noise due to other vibrations occurring in the drive shaft. It is difficult to avoid that the drive shaft resonates at the eigenvalue due to the structure of the compressor. However, even if resonance occurs, vibration can be suppressed and noise can be reduced by reducing the amount of bending of the drive shaft.

  The present invention has been made in view of such circumstances, and it is an object of the present invention to provide a compressor capable of reducing the amount of bending of a drive shaft and reducing the noise generated by the vibration caused by the bending characteristic value. With the goal.

In order to solve the above-mentioned subject, a compressor of the present invention adopts the following means.
That is, a compressor according to the present invention includes a motor portion having a compression portion, a rotor on which a plurality of metal plates having the same planar shape are stacked, and a stator provided on an outer peripheral portion of the rotor; And a drive shaft connecting the compression unit, the rotor is provided with a weight portion on a surface on one end side in the axial direction of the drive shaft, and the metal on the weight portion side among the stacked metal plates is provided The plate projects in the side direction of the stator opposite to the radial direction of the rotor with respect to the axis of the drive shaft.

  According to this configuration, since the stacked metal plates constituting the rotor project in the side direction opposite to the radial direction of the rotor from the weight portion, the metal plates project when the rotor of the motor rotates. The magnetic attraction force generated on the stator side is greater at the portion where the metal plate is not protruding. As a result, when the centrifugal force is applied by the weight portion during rotation, the magnetic attraction force is generated in the direction of relieving the bending of the drive shaft, so that the drive shaft is compared with the case where the metal plate does not protrude in the rotor You can ease the bending of the In addition, the surface of the one end side of the axial direction of the drive shaft in which a weight part is provided is a surface on the opposite side to the surface by the side of a compression part, for example.

  In the above invention, the metal plate on the weight portion side of the stacked metal plates is offset from the axis of the drive shaft in the stator side direction opposite to the weight portion in the radial direction of the rotor. It may be laminated.

  According to this configuration, since the stacked metal plates constituting the rotor are stacked so as to be shifted so as to protrude in the side direction of the stator opposite to the weight portion, when the rotor of the motor rotates, the metal plates The magnetic attraction force generated on the stator side is larger in the portion where the metal plates project and are stacked than in the portion where the metal plates project and are not stacked.

  In the above invention, in the metal plate on the weight portion side of the stacked metal plates, the weight portion protrudes in the side direction opposite to the radial direction of the rotor with respect to the axis of the drive shaft. A metal coating may be applied as well.

  According to this configuration, since the metal coating is applied so that the laminated metal plates constituting the rotor project in the side direction of the stator opposite to the weight portion, when the rotor of the motor rotates, In the portion where the metal coating is applied, the magnetic attraction force generated on the stator side is larger than the portion where the metal plate does not protrude.

  In the above invention, the weight on the weight portion side with respect to the axis of the drive shaft may be reduced in consideration of the weight of the portion of the metal plate protruding in the radial direction of the rotor.

  According to this configuration, even when the stacked metal plates project on the side opposite to the weight portion with respect to the axis of the drive shaft, the centrifugal force acting on the compression portion and the centrifugal force acting on the rotor It can be balanced.

  In the above invention, the rotor may be provided with a second weight portion on the surface on the other end side opposite to the one end side in the axial direction of the drive shaft, and among the laminated metal plates The metal plate on the second weight portion side protrudes in the side direction of the stator opposite to the radial direction of the rotor with respect to the axis of the drive shaft.

  According to this configuration, the metal plate on the second weight portion side protrudes in the side direction of the stator opposite to the radial direction of the rotor from the second weight portion, and in addition to the metal plate on the weight portion side, The magnetic attraction force generated on the stator side is larger than the portion where the metal plate does not protrude. As a result, the bending of the drive shaft can be further alleviated as compared with the case where the metal plate does not protrude in the rotor.

A compressor according to a reference example of the present invention connects a motor unit having a compression unit, a rotor on which a plurality of metal plates are stacked, and a stator provided on an outer peripheral part of the rotor, and connects the motor unit and the compression unit. A drive shaft is provided, and a weight portion is provided on a surface of the rotor opposite to the compression portion side in the axial direction of the drive shaft, and a plurality of permanent magnets are provided inside the rotor. The permanent magnet provided on the side opposite to the compression portion side in the axial direction of the drive shaft has the weight portion opposite to the axial direction of the drive shaft in the radial direction of the rotor as compared with other portions. It is arrange | positioned so that the magnetic force of stator side direction may increase.

  According to this configuration, the magnetic force of the permanent magnet is increased in the side direction of the stator opposite to the radial direction of the rotor, so that the magnetic force of the permanent magnet is increased when the rotor of the motor rotates. In one part, the magnetic attraction force generated on the stator side is larger than that in the other parts. As a result, at the time of rotation, the centrifugal force is exerted by the weight portion, and the magnetic attraction force is generated in the direction of relieving the bending of the drive shaft so that there is no part where the magnetic force of the permanent magnet is increased in the rotor. Compared to the case, the bending of the drive shaft can be alleviated.

In the above embodiment, even if the permanent magnet provided on the side opposite to the compression portion side in the axial direction of the drive shaft is biased toward the stator side in the radial direction of the rotor compared to other portions. The magnetic force may be stronger than that of the permanent magnet of another part.

  According to this configuration, since the permanent magnet is disposed on the side of the stator opposite to the radial direction of the rotor relative to the other portions, the permanent magnet is biased when the motor rotor rotates. In the disposed portion, the magnetic attraction force generated on the stator side is larger than the portion where the permanent magnet is not disposed in a biased manner. Alternatively, since the permanent magnet has a stronger magnetic force in the stator side direction opposite to the radial direction of the rotor as compared to other parts, when the motor rotor rotates, the stator in the portion where the permanent magnet has a strong magnetic force The magnetic attraction generated on the side is larger than the other parts.

  According to the present invention, it is possible to reduce the amount of bending of the drive shaft and to reduce the noise generated by the vibration caused by the bending characteristic value.

It is a longitudinal section showing a compressor concerning a 1st embodiment of the present invention. It is a cross-sectional view which shows the compression mechanism of the compressor concerning a 1st embodiment of the present invention. It is a typical longitudinal section showing a rotor and a motor of a compressor concerning a 1st embodiment of the present invention. It is a top view showing a rotor of a compressor concerning a 1st embodiment of the present invention. It is a typical longitudinal cross-sectional view which shows the 1st modification of the rotor and motor of a compressor concerning a 1st embodiment of the present invention. It is a top view which shows the 1st modification of the rotor of the compressor concerning a 1st embodiment of the present invention. It is a typical longitudinal section showing the 2nd modification of the rotor and motor of a compressor concerning a 1st embodiment of the present invention. It is a top view which shows the 2nd modification of the rotor of the compressor concerning a 1st embodiment of the present invention. It is a typical longitudinal cross-sectional view which shows the 3rd modification of the rotor and motor of a compressor concerning a 1st embodiment of the present invention. It is a top view which shows the 3rd modification of the rotor of the compressor concerning a 1st embodiment of the present invention. It is a cross-sectional view which shows the rotor and motor of a compressor which concern on the reference embodiment of this invention.

First Embodiment
Hereinafter, a compressor 1 according to a first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, the multi-cylinder rotary compressor 1 according to the present embodiment includes a cylindrical hermetic container 2 whose upper and lower portions are sealed by an upper cover 3 and a lower cover 4, and the upper side of the inside A motor 5 is installed at the site, and a compression mechanism (rotary compression mechanism) 6 driven by the motor 5 is installed at the lower site.

  A mounting leg 7 is provided on the lower periphery of the closed container 2. Further, a discharge pipe 8 penetrating the upper cover 3 is provided at the upper part of the closed container 2, and the discharge pipe 8 discharges the high pressure refrigerant gas compressed by the multi-cylinder rotary compressor 1 to the refrigeration cycle side. Furthermore, an accumulator 9 is attached to the outer peripheral portion of the closed container 2. The accumulator 9 separates liquid components such as oil and liquid refrigerant contained in low-pressure refrigerant gas returning from the refrigeration cycle side, Only a minute is sucked into the compression mechanism 6 through the suction pipes 10 and 11.

  The motor 5 includes a stator 12 and a rotor 13. The stator 12 is fixed to the inner peripheral surface of the sealed container 2 by press fitting or the like. The rotor 13 can transmit the rotational drive force of the rotor 13 to the compression mechanism 6 through the drive shaft 14 by the drive shaft 14 being coupled and integrated. Further, at the lower portion of the drive shaft 14, a first eccentric pin 15 and a second eccentric pin 16 are provided corresponding to a first roller 24 and a second roller 25 of the rotary type compression mechanism 6 described later.

  The rotary compression mechanism 6 is a two-cylinder type in the present embodiment, and the first and second compression mechanisms 6A and 6B have a first cylinder chamber 17 and a second cylinder chamber 18 formed therein. The compression mechanism 6 further includes a first cylinder body 19 and a second cylinder body 20, a partition plate (separator plate) 21, an upper bearing 22, a lower bearing 23, and the like.

  The first cylinder body 19 and the second cylinder body 20 are fixedly installed in the sealed container 2 in correspondence with the first eccentric pin 15 and the second eccentric pin 16 of the drive shaft 14. The partition plate 21 is interposed between the first cylinder main body 19 and the second cylinder main body 20, and divides the first cylinder chamber 17 and the second cylinder chamber 18. The upper bearing 22 is provided on the upper surface of the first cylinder main body 19 to define the first cylinder chamber 17 and to support the drive shaft 14. The lower bearing 23 is provided on the lower surface of the second cylinder main body 20 and defines the second cylinder chamber 18 and supports the drive shaft 14.

  The first and second compression mechanisms 6A and 6B respectively include a first roller 24 and a second roller 25 and blades 28 and 29.

  The first roller 24 and the second roller 25 are rotatably fitted to the first eccentric pin 15 and the second eccentric pin 16, respectively, and rotate in the first cylinder chamber 17 and the second cylinder chamber 18. The first eccentric pin 15 and the second eccentric pin 16 are coupled to the drive shaft 14 and integrally rotate with the drive shaft 14. The center of gravity of the second roller 25 fitted to the second eccentric pin 16 is located opposite to the center of gravity of the first roller 24 fitted to the first eccentric pin 15 with respect to the axis of the drive shaft 14.

  The blades 28 and 29 are slidably fitted in blade grooves 26 and 27 provided in the first cylinder body 19 and the second cylinder body 20, as shown in FIG. 2) Divide the inside of the cylinder chamber 18 into the suction chamber side and the discharge chamber side.

  Low pressure refrigerant gas is drawn into the first cylinder chamber 17 and the second cylinder chamber 18 of the first and second compression mechanisms 6A and 6B from the suction pipes 10 and 11 through the suction ports 30 and 31, respectively.

  The refrigerant gas sucked into the first cylinder chamber 17 and the second cylinder chamber 18 is compressed by the rotation of the first roller 24 and the second roller 25, and then, through the discharge port and the discharge valve (not shown). , And into the discharge chambers 32, 33. The refrigerant gas discharged into the discharge chambers 32, 33 is discharged into the closed container 2 and then sent out to the refrigeration cycle through the discharge pipe 8.

  The first cylinder body 19 and the second cylinder body 20 constituting the compression mechanism 6, the partition plate 21, the upper bearing 22 and the lower bearing 23 are integrally fastened and fixed via bolts. Further, the bottom of the closed container 2 is filled with refrigeration oil 34 such as PAG oil or POE oil, and the lubrication portion in the compression mechanism 6 is provided through the oil supply hole or the like provided in the drive shaft 14 Refueling is possible. An appropriate amount of extreme pressure agent adapted to each oil is added to the refrigerator oil 34. In addition, the oil supply mechanism to the compression mechanism 6 is a structure used normally, and abbreviate | omits detailed description here.

  The first balance weight 35 is provided on the upper surface of the rotor 13, that is, on one side of the drive shaft 14 in the axial direction and opposite to the side on which the compression mechanism 6 is located. Further, the center of gravity of the first balance weight 35 is located on the opposite side of the center of gravity of the first roller 24 with respect to the axis of the drive shaft 14. The second balance weight 36 is provided on the lower surface of the rotor 13, that is, on the other side of the drive shaft 14 in the axial direction and on the side where the compression mechanism 6 is located. Further, the center of gravity of the second balance weight 36 is located on the opposite side of the center of gravity of the second roller 25 with respect to the axis of the drive shaft 14.

  By providing the first balance weight 35 and the second balance weight 36 on the upper surface and the lower surface of the rotor 13, the centrifugal force applied to the first balance weight 35 and the second balance weight 36 is obtained by the first roller 24 and the second roller 25. And the centrifugal force exerted on the first roller 24 and the second roller 25 caused by the rotation of

  In the rotor 13, a plurality of steel plates are mutually insulated and stacked in the axial direction of the drive shaft 14. The steel plate is an example of a magnetic metal plate, and may be another magnetic metal plate. By laminating the steel plates, generation of eddy current is suppressed. Conventionally, the steel plates are arranged such that the outer surfaces of the rotor 13 are on the same plane. Therefore, conventionally, the interval of the gap (also referred to as an air gap) formed between the stator 12 and the rotor 13 is constant in the circumferential direction. The air gap is, for example, 100 to several tens of μm to several hundreds of μm depending on the size of the motor 5 or the like.

  On the other hand, when the rotation of the rotor 13 is stopped, the air gap according to the present embodiment is the upper side of the rotor 13, that is, one side of the drive shaft 14 in the axial direction, opposite to the side where the compression mechanism 6 is located. On the side, the air gap spacing differs between the installation side of the first balance weight 35 and the side opposite to the installation side of the first balance weight 35 with respect to the drive shaft 14. The air gap on the opposite side to the installation side of the first balance weight 35 with respect to the drive shaft 14 is narrower than the installation side of the first balance weight 35.

  For example, as shown in FIG. 3 and FIG. 4, the steel plate 13A laminated on the upper side of the rotor 13 is of the stator 12 positioned opposite to the installation side of the first balance weight 35 as compared to the other steel plates 13B. They are arranged offset so as to protrude in the direction. Here, the planar shape of the steel plate 13A and the planar shape of the steel plate 13B are the same. The shift amount of the steel plate 13A is, for example, about 1/10 of the gap of the air gap. FIG. 3 schematically shows how the rotor 13 swings with the compression mechanism 6 side as the fixed end (the same applies to FIGS. 5, 7 and 9 shown below).

  The number of shifted steel plates 13A depends on, for example, the magnetic attraction force to be increased, and is a steel plate in the range of several percent to ten and several percent on the upper side of the rotor 13. The minimum number is assumed to be one, and the maximum number is assumed to be, for example, in the range of 1/2 to 2/3 of all the steel plates. In addition, in FIG. 3, the shift amount of 13 A of steel plates is shown about the case where it is the same value in all the steel plates 13A which are shifted and arrange | positioned. The shift amount of the steel plate 13A is not limited to this example, and is not limited to the illustrated example, such as increasing the shift amount stepwise or smoothly toward the upper side.

  When the rotation of the rotor 13 is stopped by displacing the steel plates 13A stacked on the upper side of the rotor 13, the side opposite to the installation side of the first balance weight 35 with respect to the drive shaft 14 The air gap is narrower than the installation side of the first balance weight 35. As a result, since the steel plate 13A of the rotor 13 protrudes to the opposite side to the first balance weight 35, when the rotor 13 of the motor 5 rotates, the magnetic attraction force larger than the portion other than the protruding portion moves to the stator 12 side. Occur. That is, the centrifugal force is exerted by the first balance weight 35, and as described above, the steel plate 13A is disposed in a shifted manner, thereby reducing the bending of the drive shaft 14, that is, the first relative to the axis of the drive shaft 14. A magnetic attraction force is generated in the direction opposite to the balance weight 35, and the bending of the drive shaft 14 can be relieved.

  As a result, even when the drive shaft 14 resonates at the characteristic value, the amount of bending of the drive shaft 14 can be reduced as compared to the case where the steel plates are not disposed in a shifted manner, and noise generated by vibration caused by the bending characteristic value is reduced. be able to.

  The weight of the steel plate 13 of the rotor 13 may be reduced on the side of the first balance weight 35 with respect to the axis of the drive shaft 14 in consideration of the protruding portion of the steel plate 13A. 5 and 6 show an example in which the weight is reduced by forming the through holes 40 in each of the steel plates 13A.

  When the steel plates 13A are arranged in a staggered manner, it is possible to increase the magnetic attraction force, but the balance with the centrifugal force applied to the first roller 24 and the second roller 25 is greater than when the steel plates 13A are not displaced. Can be worse. In addition, since the weight of the protruding portion is smaller than the weight of the first balance weight 35, it is estimated that the rate of deterioration of the balance is not so large.

  As shown in FIG. 5 and FIG. 6, by forming the through holes 40, the first roller 24 and the second roller 24 generated by the centrifugal force applied above the rotor 13 and the rotation of the first roller 24 and the second roller 25. The balance with the centrifugal force applied to the roller 25 can be maintained.

  5 and 6 show the case where the through holes 40 are provided in all of the steel plates 13A protruding in the direction of the stator 12 located on the opposite side to the first balance weight 35, but the present invention is not limited to this. It is not limited to the example. That is, the through hole 40 may be installed in a part of the steel plate 13A. Further, instead of providing the through holes 40 in the steel plate 13A, the weight itself of the first balance weight 35 may be reduced in consideration of the protruding portion of the steel plate 13A.

As mentioned above, although the compressor concerning a 1st embodiment of the present invention was explained, the present invention is not limited to the composition of the embodiment mentioned above.
For example, in the embodiment described above, an example is described in which the air gap is narrowed on the upper side of the rotor 13 in order to reduce bending caused by the centrifugal force of the first balance weight 35, but the present invention is limited to this example I will not.

  For example, as shown in FIGS. 7 and 8, the steel plate 13C stacked on the lower side of the rotor 13 is a stator opposite to the side on which the second balance weight 36 is installed, as compared to the steel plate 13B of the other intermediate portion. It may be arranged in a staggered manner so as to protrude to the 12 side. Thereby, when the rotation of the rotor 13 is stopped, the lower side of the rotor 13, that is, the other side in the axial direction of the drive shaft 14, on the side where the compression mechanism 6 is positioned, The air gap on the opposite side to the installation side of the two balance weights 36 is narrower than the installation side of the second balance weights 36.

  As a result, since the steel plate 13C of the rotor 13 protrudes to the opposite side to the second balance weight 36, when the rotor 13 of the motor 5 rotates, the magnetic attraction force larger than the portion other than the protruding portion moves to the stator 12 side. Occur. That is, a centrifugal force is exerted by the second balance weight 36 to bend the drive shaft 14, and as described above, the steel plate 13C is disposed in a shifted manner, thereby reducing the bending of the drive shaft 14, ie, the drive shaft A magnetic attraction force is generated in the radial direction opposite to the second balance weight 36 with respect to the axis of 14, and the bending of the drive shaft 14 can be relaxed.

  As described above, when the drive shaft 14 resonates at a specific value by displacing the steel plates 13C of the rotor 13, the bending amount of the drive shaft 14 can be reduced, and if it is shifted together with the steel plate 13A of the rotor 13, the bending specific value It is possible to further reduce the noise generated by the vibration caused by the If the amount of bending of the drive shaft 14 on the lower side of the rotor 13 is larger, only the steel plate 13C of the rotor 13 may be shifted.

  Further, in the above-described embodiment, the steel plates 13A stacked on the upper side of the rotor 13 are offset from the other steel plates so as to protrude on the opposite side to the installation side of the first balance weight 35. However, the invention is not limited to this example. That is, when the rotation of the rotor 13 is stopped, the air gap on the opposite side to the installation side of the first balance weight 35 with respect to the drive shaft 14 is narrowed compared to the installation side of the first balance weight 35 For example, as shown in FIGS. 9 and 10, the protruding portion 41 may be provided by separately coating the outer peripheral portion of the steel plate 13A. In this case, the protruding portion 41 is formed of silver paste or the like. Alternatively, the projecting portion 41 may be formed so that the planar shape itself of the steel plate 13A is different from the shape of the steel plate 13B of the other portion.

  The projecting portion 41 is formed on the side opposite to the installation side of the first balance weight 35 with respect to the drive shaft 14 among the stacked steel plates 13A. Thus, when the rotation of the rotor 13 is stopped, the air gap on the opposite side of the drive shaft 14 to the first balance weight 35 installation side is narrower than the first balance weight 35 installation side. As a result, since the protruding portion 41 of the steel plate 13A of the rotor 13 protrudes to the opposite side to the first balance weight 35, when the rotor 13 of the motor 5 rotates, the magnetic attraction force larger than the portions other than the protruding portion 41 Occurs on the stator 12 side. That is, a centrifugal force is exerted by the first balance weight 35 and bending occurs in the drive shaft 14. By forming the projecting portion 41 as described above, the direction in which the bending of the drive shaft 14 is alleviated, ie, the drive shaft 14 The magnetic attraction force is generated in the direction of the side of the stator 12 opposite to the first balance weight 35 with respect to the axis of the shaft, and the bending of the drive shaft 14 can be relaxed.

  As a result, even when the drive shaft 14 resonates at the characteristic value, the amount of bending of the drive shaft 14 can be reduced, and the noise generated by the vibration caused by the bending characteristic value can be reduced.

[ Reference embodiment]
Next, a compressor according to a reference embodiment of the present invention will be described. The compressor according to the present embodiment is different from the compressor according to the above-described first embodiment in that the rotor 13 is different. Therefore, the rotor 13 according to the present embodiment will be described below. Components other than the rotor 13 are the same as those in the first embodiment, and thus detailed description will be omitted.

  In the rotor 13, a plurality of steel plates are mutually insulated and stacked in the axial direction of the drive shaft 14. By laminating the steel plates, generation of eddy current is suppressed. The steel plates according to the present embodiment are arranged such that the outer surfaces of the rotor 13 are on the same plane. Therefore, the gap (air gap) formed between the stator 12 and the rotor 13 is constant in the circumferential direction.

  Permanent magnets 42 and 50 are embedded in the rotor 13. Although an arrangement example of the permanent magnets 42 and 50 is shown in FIG. 11, the size, position, orientation and the like of the permanent magnets arranged inside the rotor 13 are not limited to the arrangement example shown in FIG.

  The permanent magnets 42, 50 are disposed in the openings formed in the steel plate. In the steel plate 13D stacked on the upper side of the rotor 13, the permanent magnet 42 is located on the opposite side of the first balance weight 35 on the side where the first balance weight 35 is installed, as compared with the permanent magnet 50 installed on the other steel plate 13E. It is arranged by shifting in the direction. Here, the planar shape of the steel plate 13D and the planar shape of the steel plate 13E are the same.

  That is, the plurality of permanent magnets 50 provided other than the upper side of the rotor 13 are point-symmetrically provided centering on the axis of the drive shaft 14 similarly to the arrangement of the permanent magnets in the conventional rotor. On the other hand, as described above, the plurality of permanent magnets 42 provided on the upper side of the rotor 13 are offset to the side opposite to the installation side of the first balance weight 35, and the center of the point symmetry of the permanent magnet 42 Also, with respect to the axis of the drive shaft 14, the first balance weight 35 is offset to the side opposite to the installation side.

  As a result, when the rotor 13 of the motor 5 rotates, a magnetic attraction force that is greater on the upper side of the rotor 13 than on the side other than the upper side of the rotor 13 is generated on the stator 12 side. That is, a centrifugal force is exerted by the first balance weight 35 to cause bending of the drive shaft 14, and the permanent magnet 42 is displaced as described above, thereby reducing the bending of the drive shaft 14, that is, driving A magnetic attraction force is generated in the radial direction opposite to the first balance weight 35 with respect to the axis of the shaft 14 and the bending of the drive shaft 14 can be relaxed.

  As a result, even when the drive shaft 14 resonates at the characteristic value, the amount of bending of the drive shaft 14 can be reduced, and the noise generated by the vibration caused by the bending characteristic value can be reduced.

As described above, in the compressor according to the reference embodiment of the present invention, an example in which the installation position of the permanent magnet 42 is shifted on the upper side of the rotor 13 has been described to reduce bending generated by centrifugal force of the first balance weight 35. The invention is not limited to this example.

  That is, on the upper side of the rotor 13, the magnetic attraction force may be increased in the direction in which the bending of the drive shaft 14 is relieved, that is, in the radial direction opposite to the first balance weight 35 with respect to the axis of the drive shaft 14. For example, the magnetic force of the permanent magnet disposed opposite to the first balance weight 35 with respect to the axis of the drive shaft 14 is stronger than the permanent magnet disposed on the first balance weight 35 with respect to the axis of the drive shaft 14.

  Also in this case, a magnetic attraction force is generated in the direction to ease the bending of the drive shaft 14, that is, in the radial direction opposite to the first balance weight 35 with respect to the axis of the drive shaft 14, and the bending of the drive shaft 14 can be relaxed.

  Further, in the embodiment described above, the permanent magnet 42 disposed on the upper side of the rotor 13 is disposed so that the magnetic attraction force increases in the radial direction opposite to the first balance weight 35 with respect to the axis of the drive shaft 14 Although the example has been described, the permanent magnets disposed below the rotor 13 may be similarly disposed. In this case, the permanent magnets disposed below the rotor 13 are disposed such that the magnetic attraction force increases in the opposite radial direction of the second balance weight 36 with respect to the axis of the drive shaft 14.

Furthermore, although the compressor according to the first and reference embodiments described above has been described for the case of a multi-cylinder rotary compressor, the present invention is not limited to this type of compressor. For example, the present invention can also be applied to a rotary compressor provided with only one rotary compression mechanism, and can also be applied to a scroll compressor provided with one or more scroll compression mechanisms.

1 Compressor 2 Sealed container 5 Motor (Motor section)
6 Compression mechanism (compression unit)
6A first compression mechanism 6B second compression mechanism 8 discharge piping 9 accumulator 10, 11 suction piping 12 stator 13 rotors 13A, 13B, 13C, 13D, 13E steel plate 14 drive shaft 15 first eccentric pin 16 second eccentric pin 17 first Cylinder chamber 18 Second cylinder chamber 19 First cylinder body 20 Second cylinder body 24 First roller 25 Second roller 35 First balance weight (weight part)
36 Second balance weight (second weight)
40 through hole 41 projecting portion 42, 50 permanent magnet

Claims (5)

A compression unit,
A motor unit having a rotor in which a plurality of metal plates having the same planar shape are stacked and a stator provided on an outer peripheral portion of the rotor;
A drive shaft connecting the motor unit and the compression unit;
Equipped with
The rotor is provided with a weight portion on a surface on one end side in the axial direction of the drive shaft,
The said metal plate by the side of the said weight part among the metal plates laminated | stacked is a compressor which protrudes in the said stator side direction opposite to the radial direction of the said rotor with respect to the axial line of the said drive shaft.   Among the metal plates stacked, the metal plate on the weight portion side is stacked with being shifted in the direction of the stator opposite to the radial direction of the rotor with respect to the axis of the drive shaft. The compressor according to claim 1.   The metal plate on the weight portion side of the stacked metal plates is made of metal so as to protrude in the stator side direction opposite to the weight portion in the radial direction of the rotor with respect to the axis of the drive shaft The compressor according to claim 1, wherein a coating is applied.   The weight on the weight portion side with respect to the axis of the drive shaft is reduced in consideration of the weight of the radially projecting portion of the rotor of the metal plate. Description compressor. A second weight portion is provided on the rotor at a surface on the other end side opposite to the one end side in the axial direction of the drive shaft,
The metal plate on the second weight portion side of the stacked metal plates protrudes in the side direction of the stator opposite to the radial direction of the rotor with respect to the axis line of the drive shaft. The compressor according to any one of claims 1 to 4.

Images