WO2015083656A1

WO2015083656A1 - Compressor

Info

Publication number: WO2015083656A1
Application number: PCT/JP2014/081707
Authority: WO
Inventors: 和慶土田
Original assignee: 三菱電機株式会社
Priority date: 2013-12-05
Filing date: 2014-12-01
Publication date: 2015-06-11
Also published as: CN105992872A; CN105992872B; JPWO2015083656A1; WO2015083261A1; JP6038351B2

Abstract

A compressor (100) is provided with an electric motor (1) and a compression mechanism (103) which is driven by the electric motor (1). The electric motor includes a stator (3) and a rotor (5) which is rotatably provided facing the stator (3). The air gap (15) between the stator (3) and the rotor (5) is nonuniform circumferentially. The rotor may be configured either in such a manner that the outer peripheral shape of the rotor is point-symmetrical and the center (EC) of the point-symmetrical outer peripheral shape and the center (RC) of rotation of the rotor are offset from each other or in such a manner that the outer peripheral shape of the rotor is not point-symmetrical.

Description

Compressor

The present invention relates to a compressor.

Patent Document 1 discloses an electric motor that drives a compression mechanism in a compressor. In such an electric motor for a compressor, a member called a balance weight is attached to the rotor in order to reduce vibration and noise generated with the rotation of the eccentric portion of the compression mechanism.

Japanese Patent Laid-Open No. 9-200986

In general, a non-magnetic material is used for the balance weight described above so as not to reduce the magnetic force generated in the electric motor. However, it is ideal if vibration and noise during rotation can be reduced without providing a balance weight.

The present invention has been made in view of the above, and it is an object of the present invention to provide a compressor capable of reducing the vibration generated with the rotation of the eccentric portion of the compression mechanism without depending on a dedicated vibration suppressing member. Objective.

In order to achieve the above-described object, a compressor according to the present invention is a compressor including an electric motor and a compression mechanism driven by the electric motor, and the electric motor rotates in opposition to the stator and the stator. A rotor provided in a possible manner, the rotor including a first portion and a second portion arranged in a direction in which the rotation center RC of the rotor extends, an air gap between the first portion and the stator, and The air gap between the second part and the stator is non-uniform in the circumferential direction, the outer peripheral shapes of the first part and the second part are point-symmetric, and the point The outer peripheral center of the symmetrical outer peripheral shape is shifted from the rotational center RC of the rotor, and the outer peripheral center of the first part and the outer peripheral center of the second part are the rotational center of the rotor as viewed from the side. R Across, it is located opposite to each other.

According to the compressor of the present invention, it is possible to reduce the vibration generated with the rotation of the eccentric portion of the compression mechanism without depending on the dedicated vibration suppressing member.

It is a longitudinal cross-sectional view of the rotary compressor which concerns on Embodiment 1 of this invention. It is a figure which shows an internal structure at the time of seeing an electric motor on the surface which makes a rotating shaft line a perpendicular line. It is a figure which shows the rotor single-piece | unit in FIG. It is a figure which shows the rotor single-piece | unit of FIG. 3 from the side. It is a figure of the same aspect as FIG. 4 regarding Embodiment 2 of this invention. It is a figure which shows the structure of the rotor core seen from the arrow VI of FIG. It is a figure which shows the shaft containing a piston. It is a figure which shows the rotor provided with the balance weight. It is a figure which shows the structure which combined the shaft of FIG. 7, and the rotor of FIG. It is a figure which shows the integral rotating structure of a rotor, a piston, and a rotating shaft (shaft) regarding Embodiment 2 of this invention. It is a figure of the same aspect as FIG. 5 regarding Embodiment 3 of this invention. It is a figure which shows the structure of the rotor core seen from the arrow VIII of FIG. It is a figure of the same aspect as FIG. 3 regarding Embodiment 4 of this invention. It is a figure which extracts and shows only the outer periphery shape of a rotor core regarding this Embodiment 4. FIG. It is a figure of the same aspect as FIG. 13 regarding Embodiment 5 of this invention. It is a figure of the same aspect as FIG.13 and FIG.14 regarding this Embodiment 5. FIG. It is a figure of the same aspect as FIG. 15 regarding Embodiment 6 of this invention. It is a figure of the same aspect as FIG. 16 regarding this Embodiment 6. FIG. It is a figure of the same aspect as FIG. 17 regarding Embodiment 7 of this invention. It is a figure of the same aspect as FIG. 18 regarding this Embodiment 7. FIG.

Hereinafter, an embodiment when the present invention is applied to a rotary compressor will be described with reference to the accompanying drawings. In the drawings, the same reference numerals indicate the same or corresponding parts.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 of the present invention. The type of the compressor of the present invention is not limited to the rotary compressor.

The rotary compressor 100 includes an electric motor 1 and a compression mechanism 103 in a sealed container 101. Although not shown in the figure, refrigeration oil that lubricates each sliding portion of the compression mechanism 103 is stored at the bottom of the sealed container 101.

The compression mechanism 103 includes, as main elements, a cylinder 104, a rotation shaft 107 (shaft 13 described later) that is a shaft that is rotated by the electric motor 1, a piston 109 that is fitted into the rotation shaft 107, and a suction side inside the cylinder 104. And a vane (not shown) that is divided into a compression side, a pair of upper and

lower frames

111 and 113, and a pair of upper and

lower frames

111 and 113, in which a rotating shaft 107 is rotatably inserted and closes the upper and lower ends of the cylinder 104 The muffler 115 attached to the frame 113 is included.

The stator 3 of the electric motor 1 is directly attached and held on the sealed container 101 by a method such as shrink fitting or welding. Electric power is supplied to the coil of the stator 3 from a glass terminal fixed to the sealed container 101.

The rotor 5 is disposed on the inner diameter side of the stator 3 via a gap, and is freely rotatable by the bearing portions (the upper frame 111 and the lower frame 113) of the compression mechanism 103 via the rotation shaft 107 at the center of the rotor 5. It is held in the correct state.

Next, the electric motor 1 related to the first embodiment will be described. FIG. 2 is a diagram illustrating an internal configuration when the electric motor is viewed from a plane having a rotation axis as a perpendicular line. FIG. 3 is a diagram showing a single rotor in FIG. FIG. 4 is a view showing the rotor of FIG. 3 from the side.

The electric motor 1 includes a stator 3 and a rotor 5 that is rotatably provided to face the stator. The stator 3 includes a stator core 17 having a plurality of tooth portions 7. Each of the plurality of tooth portions 7 is adjacent to another tooth portion 7 via a corresponding slot portion 9. The plurality of tooth portions 7 and the plurality of slot portions 9 are arranged so as to be alternately arranged at equal intervals in the circumferential direction. A known stator winding (not shown) is wound around each of the plurality of tooth portions 7 in a known manner.

Each of the tooth portions 7 extends in the radial direction and protrudes toward the rotation center RC. Further, most of the tooth portion 7 has a substantially equal circumferential width from the radially outer side to the radially inner side, but the tooth tip portion is located at the tip end that is the radially inner side of the tooth portion 7. 7a. Each of the tooth tip portions 7a is formed in an umbrella shape in which both side portions extend in the circumferential direction. Furthermore, the front end surface of the tooth tooth tip portion 7a is curved in an arc shape.

The rotor 5 has a rotor core 11 and a shaft 13. The shaft 13 is connected to the rotor core 11 by shrink fitting, press fitting, or the like, and transmits rotational energy to the rotor core 11. An air gap 15 is secured between the outer peripheral surface of the rotor 5 and the inner peripheral surface of the stator 3.

The rotor core 11 and the stator core 17 are configured by punching a predetermined thickness of an electromagnetic steel sheet into a required shape and laminating a predetermined number of electromagnetic steel sheets while being fastened with caulking.

The rotor core 11 is provided with a plurality of permanent magnets (not shown). The installation mode of the permanent magnet is not particularly limited and may be a known mode. For example, the plurality of permanent magnets may be attached to the outer surface of the rotor core 11 or embedded in the rotor core 11.

As shown in FIGS. 2 to 4, the electric motor 1 has a rotation center RC. The rotor 5 rotates around the rotation center RC. Further, the arcuate curvature of the tip surfaces of the plurality of teeth tooth tips 7a described above is formed so as to be positioned on one circle centered on the rotation center RC. Furthermore, the outer diameter of the shaft 13 and the inner diameter of the rotor core 11 are defined by a circle centered on the rotation center RC. On the other hand, the electric motor 1 has a rotor outer circumferential center EC which is the center (centroid) of the circular outer shape of the rotor core 11. The rotor outer circumferential center EC is shifted in the radial direction with respect to the rotation center RC. That is, as for the rotor 5, the center of outer peripheral shape is eccentric with respect to the center of rotation.

Next, the operation of the rotary compressor 100 will be described. The refrigerant gas supplied from the accumulator 117 is sucked into the cylinder 104 through a suction pipe 119 fixed to the hermetic container 101. When the electric motor 1 is rotated by energization of the inverter, the piston 109 fitted to the rotating shaft 107 is rotated in the cylinder 104. Thereby, the refrigerant is compressed in the cylinder 104. After the refrigerant passes through the muffler 115, the refrigerant rises in the sealed container 101. At this time, refrigeration oil is mixed in the compressed refrigerant. When the mixture of the refrigerant and the refrigerating machine oil passes through the air holes provided in the rotor core 11, the separation of the refrigerant and the refrigerating machine oil is promoted, and the refrigerating machine oil can be prevented from flowing into the discharge pipe 121. In this way, the compressed refrigerant is supplied to the high-pressure side of the refrigeration cycle through the discharge pipe 121 provided in the sealed container 101.

In the first embodiment, as described above, the center of the outer peripheral shape of the rotor 5 is eccentric with respect to the center of rotation of the rotor 5. For this reason, while the compressor is driven, the rotor 5 rotates while swinging, and the air gap 15 between the stator 3 and the rotor 5 is not uniform in the circumferential direction, that is, nonuniform in the circumferential direction. As a result, an imbalance occurs with respect to the magnetic attractive force acting on the rotor 5, and it is possible to reduce the vibration generated with the rotation of the eccentric portion of the compression mechanism 103 of the compressor, and the balance is a dedicated member for suppressing vibration. Weights can be deleted or reduced. Further, in the first embodiment, in the rotor having a symmetrical outer periphery shape, the shape between the rotor outer periphery and the inner periphery such as a magnet insertion hole is used in order to use the unbalance of the magnetic attractive force caused by the rotor swinging around. Implementation is possible without any relation.

When separating the rotor outer circumference center EC and the rotation center RC, considering the press accuracy of the mold, the distance of the deviation between the rotor outer circumference center EC and the rotation center RC should be 5% or more of the laminated plate thickness. Would be feasible.

As described above, according to the compressor and the vibration reduction method of the compressor according to the first embodiment, the vibration generated with the rotation of the eccentric portion of the compression mechanism without depending on the dedicated vibration suppressing member. Can be reduced.

Embodiment 2. FIG.
Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 5 is a diagram of the same mode as FIG. 4 regarding the second embodiment. FIG. 6 is a diagram showing the configuration of the rotor core as seen from the arrow VI in FIG. 3 illustrates the first embodiment, the configuration of the rotor core as seen from the arrow III in FIG. 5 is the same as that in FIG. 3 with respect to the second embodiment. In addition, this Embodiment 2 shall be comprised similarly to the said Embodiment 1 except the part demonstrated below.

In the second embodiment, the rotor 105 of the electric motor provided in the compressor includes a rotor core 11a as a first step portion (first portion) aligned in the direction in which the rotation center RC extends and a second step portion (first step). And a rotor core 11b as two parts). The air gap between the rotor core 11a that is the first part and the stator 3 and the air gap between the rotor core 11b that is the second part and the stator 3 are nonuniform in the circumferential direction, respectively. The outer peripheral shapes of the rotor core 11a and the rotor core 11b are point-symmetric. Further, the rotor outer periphery center ECa of the rotor core 11a and the rotor rotation center RC are shifted from each other, and the rotor outer periphery center ECb of the rotor core 11b and the rotor rotation center RC are shifted from each other. The rotor outer periphery center ECa of the rotor core 11a as the first step portion and the rotor outer periphery center ECb of the rotor core 11b as the second step portion are opposite to each other across the rotation center RC (an example). Is 180 opposite). As an example, the

rotor cores

11a and 11b are provided as portions having the same height dimension (dimension in the direction in which the rotation center RC extends).

Further, the excellent advantages of the second embodiment configured as described above will be described. First, a piston functioning as an eccentric portion will be described with reference to FIGS. FIG. 7 shows a shaft including a piston. Since the center axis PC of the piston 109 is in an eccentric position with respect to the rotation center RC of the rotation shaft 107 (shaft 13), when the rotation shaft 107 (shaft 13) rotates about the rotation center RC, the piston 109 Centrifugal force acts in the eccentric direction (arrow direction in FIG. 7). For this reason, the rotating shaft 107 (shaft 13) exerts a force that swings around during rotation.

Here, as one of the methods for reducing the above-described vibration during rotation, there is a method using a rotor provided with a balance weight as shown in FIG. As shown in FIG. 8, a balance weight 6 'made of a non-magnetic member having a large specific gravity is attached to both end surfaces in the axial direction of the rotor 5'.

FIG. 9 shows a configuration in which the shaft of FIG. 7 and the rotor of FIG. 8 are combined. As shown in FIG. 9, the balance weight 6 ′ attached above the rotor 5 ′ and the balance weight 6 ′ attached below the rotor 5 ′ have a center of gravity as viewed from the side as shown in FIG. 9. The positions are biased so that they do not line up and down. Further, the center of gravity of the balance weight 6 ′ attached above the rotor 5 ′ and the center of gravity of the balance weight 6 ′ attached below the rotor 5 ′ are both offset from the rotation center RC of the rotating shaft. For this reason, at the time of rotation, centrifugal force acts on each balance weight 6 ′ of the rotor 5 ′ as described for the piston.

For this reason, in the integral rotating structure including the balance weight 6 ′, the rotor 5 ′ and the piston as shown in FIG. 9, a centrifugal force as indicated by an arrow acts on each of the balance weight 6 ′ and the piston. As a result, the centrifugal force in the piston is canceled by the centrifugal force in the balance weight 6 ', and the integral rotating structure, as a whole, suppresses the force that swings around during rotation, and promotes low vibration and low noise. Yes.

However, the vibration / noise reduction technique based on the existence of such balance weights involves other problems such as an increase in the size of the rotor, an increase in the weight of the rotor, and an increase in cost. Therefore, it is very preferable if the vibration generated with the rotation of the eccentric portion of the compression mechanism can be reduced without depending on a dedicated vibration suppressing member only for vibration suppressing action such as a balance weight.

Therefore, in the second embodiment, the above-described rotor 105 is used. FIG. 10 is a diagram showing an integral rotating structure of a rotor, a piston, and a rotating shaft (shaft) in the second embodiment.

As shown in FIG. 10, in the second embodiment, the rotor outer circumference center ECa of the rotor core 11a and the rotation center RC of the rotor are deviated, and the rotor outer circumference center ECb of the rotor core 11b is rotated with the rotation of the rotor. The rotor outer periphery center ECa of the rotor core 11a and the rotor outer periphery center ECb of the rotor core 11b are shifted from each other in opposite directions with respect to the rotation center RC.

In particular, in a preferred example of the second embodiment, as shown in FIG. 10, the rotor core 11 b as the second part is between the rotor core 11 a as the first part and the piston 109 (the direction in which the rotation center RC extends). The rotor outer circumferential center ECa of the rotor core 11a and the central axis PC of the piston 109 are on the same side with respect to the rotation center RC (see FIG. 10). The rotor outer circumferential center ECb of the rotor core 11b is located on the opposite side of the rotor outer circumferential center ECa of the rotor core 11a and the central axis PC of the piston 109 (in FIG. 10) across the rotation center RC. (Right side of the center of rotation RC).

According to the eccentric rotary structure as shown in FIG. 10, the rotor 105 itself can produce an action of canceling the centrifugal force acting on the piston 109, thereby greatly increasing the balance weight provided to the rotor 105. The vibration can be reduced even if it is reduced to, or the vibration can be reduced without providing a balance weight itself.

Further, the fact that the rotor outer circumference center ECa of the rotor core 11a and the rotor outer circumference center ECb of the rotor core 11b are shifted from the rotation center RC of the rotor simply means that the center of gravity position of the rotor core 11a and the center of gravity of the rotor core 11b are the rotation center of the rotor. Not only does it deviate from the RC, but there is also a difference between how the air gap between the rotor core 11 a and the stator 3 is biased and how the air gap between the rotor core 11 b and the stator 3 is biased. That is, vibrations can be reduced by utilizing not only the force caused by the inertial force (center of gravity position) but also the force caused by magnetism (air gap). That is, in each of the rotor core 11a and the rotor core 11b, the air gap between the rotor and the stator 3 is non-uniform in the circumferential direction, and in each of the rotor core 11a and the rotor core 11b, the magnetic gap is changed according to the non-uniform mode of the air gap. Magnetic imbalance due to resistance difference occurs. Due to this magnetic imbalance, a magnetic attractive force in the same direction as the centrifugal force due to the above-described center of gravity position acts on each of the rotor core 11a and the rotor core 11b. Therefore, these magnetic attractive forces also act to cancel out the centrifugal force of the piston, thereby promoting low vibration and low noise.

Such Embodiment 2 can also reduce the vibration generated with the rotation of the eccentric part of the compression mechanism without depending on the dedicated vibration suppressing member.

Embodiment 3 FIG.
Next, a third embodiment of the present invention will be described based on FIGS. FIG. 11 is a diagram of the same mode as FIG. 4 and FIG. 5 regarding the third embodiment. FIG. 12 is a diagram showing the configuration of the rotor core as seen from the arrow VIII in FIG. Further, with respect to the third embodiment, the configuration of the rotor core viewed from the arrow III in FIG. 11 is the same as that in FIG. 3, and the configuration of the rotor core viewed from the arrow VI in FIG. In addition, this Embodiment 3 shall be comprised similarly to the said Embodiment 2 except the part demonstrated below.

In the third embodiment, the rotor 205 of the electric motor provided in the compressor has a rotor core 11a as a first step portion (first portion) arranged in the following order in the direction in which the rotation center RC extends, a third step. A rotor core 11c as a part and a rotor core 11b as a second step part (second part). In the

rotor cores

11a and 11b, the rotor outer circumferential centers ECa and ECb are both displaced in the radial direction with respect to the rotation center RC, but the rotor outer circumferential center ECa of the rotor core 11a as the first step portion and the second step portion. The rotor outer circumference center ECb of the rotor core 11b is shifted in the opposite direction (for example, opposite to 180) across the rotation center RC. Further, the rotor core 11c as the third step portion is located between the rotor core 11a as the first step portion and the rotor core 11b as the second step portion, and the rotor outer circumference center of the rotor core 11c as the third step portion ECc coincides with the rotation center RC. In addition, although it is an example, the

rotor cores

11a and 11b are provided as a part of the same height dimension, and the height dimension of the rotor core 11c as a 3rd step part is the rotor core 11a and 2nd as a 1st step part. It is larger than the height dimension of the rotor core 11b as the stepped portion.

Also according to the third embodiment, the vibration generated with the rotation of the eccentric portion of the compression mechanism can be reduced without depending on the dedicated vibration suppressing member as in the first embodiment. Further, the rotor core 11a and the rotor core 11b of FIG. 11 of the third embodiment also function in the same manner as the rotor core 11a and the rotor core 11b of FIG. 5 of the second embodiment. Advantages similar to those of Embodiment 2 are obtained.

Embodiment 4 FIG.
In the present invention, the air gap between the theta and the rotor is not uniform in the circumferential direction. As a first aspect, the rotor outer shape is point-symmetric and the point-symmetric outer shape rotor. It may be achieved that the outer periphery center and the rotation center are deviated. That is, in the present invention, as a first aspect, when viewed from a plane having a rotation axis as a perpendicular line, the outer peripheral shape of the rotor is point-symmetric, and the rotor outer peripheral center and the rotational center of the point-symmetric outer peripheral shape are This is a compressor vibration reduction method in which the air gap between the data and the rotor is nonuniform in the circumferential direction due to the deviation. Embodiments 1 to 3 described above are examples of the first aspect. The fourth embodiment will be described as another example of the first aspect. In addition, this Embodiment 4 shall be comprised similarly to the said Embodiment 1 except the part demonstrated below.

FIG. 13 is a diagram of the same mode as FIG. 3 regarding the fourth embodiment. FIG. 14 is a diagram showing only the outer peripheral shape of the rotor core in the fourth embodiment. As shown in FIG. 13, the rotor core 11 d has a plurality of notches 51 formed on the outer peripheral surface thereof, but the outer peripheral shape is point-symmetric with respect to the rotor outer peripheral center EC as shown in FIG. 14. It has become. Such a rotor core 11d is combined with the shaft 13, and as shown in FIG. 13, the rotor outer circumferential center EC is shifted in the radial direction with respect to the rotation center RC.

Also in this fourth embodiment, as in the first embodiment, it is possible to reduce the vibration generated with the rotation of the eccentric portion of the compression mechanism without depending on the dedicated vibration suppressing member.

Embodiment 5 FIG.
The fifth embodiment is an example of the first aspect, and is an example different from the first to fourth embodiments. FIGS. 15 and 16 are views of the same mode as FIGS. 13 and 14 regarding the fifth embodiment. In addition, this Embodiment 5 shall be comprised similarly to the said Embodiment 1 except the part demonstrated below.

As shown in FIG. 15, the rotor core 11e has a plurality of protrusions (bulges) 53 formed on the outer peripheral surface thereof, but the outer peripheral shape thereof is the rotor outer peripheral center EC as shown in FIG. Is point-symmetric. Such a rotor core 11e is combined with the shaft 13, and as shown in FIG. 15, the rotor outer circumferential center EC is shifted in the radial direction with respect to the rotation center RC. In addition, although the protrusion part 53 has a circular arc shape whose diameter is smaller than outer peripheral parts other than the protrusion part 53 of the rotor core 11e, it is not limited to this.

Also in this fifth embodiment, the vibration generated with the rotation of the eccentric portion of the compression mechanism can be reduced without depending on the dedicated vibration suppressing member, as in the first embodiment.

It should be noted that both the above-described fourth and fifth embodiments can be implemented in combination with the above-described second and third embodiments. That is, each rotor core in the fourth and fifth embodiments may be used as one or both of the rotor core 11a as the first step portion and the rotor core 11b as the second step portion in the second or third embodiment. Good.

Embodiment 6 FIG.
In the present invention, the non-uniform air gap between the data and the rotor in the circumferential direction is achieved as a second aspect by using a rotor whose outer peripheral shape is asymmetric with respect to the rotation center RC. It may be. That is, the second aspect of the present invention is that the air gap between the rotor and the rotor is circumferential in the circumferential direction by using a rotor whose outer peripheral shape is asymmetric with respect to the axis of rotation when viewed from the plane having the rotation axis as a perpendicular line. This is a method of reducing the vibration of the compressor, which is non-uniform over the whole area. And this Embodiment 6 is demonstrated as an example of this 2nd aspect. FIGS. 17 and 18 are views of the same mode as FIGS. 15 and 16 regarding the sixth embodiment. In addition, this Embodiment 6 shall be comprised similarly to the said Embodiment 1 except the part demonstrated below.

As shown in FIG. 17, the rotor core 11f has only one protrusion (swelled portion) 55 formed on the outer peripheral surface thereof. Therefore, the outer peripheral shape of the rotor core 11f is asymmetrical as shown in FIG. In addition, although the protrusion part 55 has a circular arc shape whose diameter is smaller than outer peripheral parts other than the protrusion part 55 of the rotor core 11f, it is not limited to this. Further, when considering the approximate point-symmetric outer peripheral shape X having the largest overlapping range with the outer peripheral shape of the rotor core 11f, the rotor outer peripheral center EC of the approximate point-symmetric outer peripheral shape X coincides with the rotation center RC in the illustration of FIG. However, the sixth embodiment is not limited to this, and the rotor outer circumference center EC may be displaced in the radial direction with respect to the rotation center RC.

Also in this sixth embodiment, as in the first embodiment, it is possible to reduce the vibration generated with the rotation of the eccentric portion of the compression mechanism without depending on the dedicated vibration suppressing member.

Embodiment 7 FIG.
The seventh embodiment is an example of the second aspect, and is an example further different from the sixth embodiment. 19 and 20 are views of the same mode as in FIGS. 17 and 18 regarding the seventh embodiment. In addition, this Embodiment 7 shall be comprised similarly to the said Embodiment 1 except the part demonstrated below.

As shown in FIG. 19, the rotor core 11g has a plurality of protrusions (bulges) 57 formed on the outer peripheral surface thereof, but the outer peripheral shape of the rotor core 11g is astigmatic as shown in FIG. It is symmetrical. In addition, although the protrusion part 57 has a circular arc shape with a diameter smaller than outer peripheral parts other than the protrusion part 57 of the rotor core 11g, it is not limited to this. Further, when considering the approximate point-symmetric outer peripheral shape X having the largest overlapping range with the outer peripheral shape of the rotor core 11g, the rotor outer peripheral center EC of the approximate point-symmetric outer peripheral shape X matches the rotational center RC in the illustration of FIG. However, the sixth embodiment is not limited to this, and the rotor outer circumference center EC may be displaced in the radial direction with respect to the rotation center RC.

Also according to the seventh embodiment, the vibration generated with the rotation of the eccentric portion of the compression mechanism can be reduced without depending on the dedicated vibration suppressing member as in the first embodiment.

Although the contents of the present invention have been specifically described with reference to the preferred embodiments, various modifications can be made by those skilled in the art based on the basic technical idea and teachings of the present invention. It is self-explanatory.

1 electric motor, 3 stator, 105, 205 rotor, 11 rotor core, 15 air gap, 100 rotary compressor, 103 compression mechanism, 107 rotating shaft, 109 piston.

Claims

A compressor comprising an electric motor and a compression mechanism driven by the electric motor,
The electric motor includes a stator and a rotor that is rotatably provided to face the stator,
The rotor includes a first portion and a second portion that are aligned in a direction in which the rotation center RC of the rotor extends.
The air gap between the first part and the stator and the air gap between the second part and the stator are each non-uniform over the circumferential direction,
Each of the outer peripheral shapes of the first part and the second part is point-symmetric, and the outer peripheral center of the point-symmetric outer peripheral shape is shifted from the rotation center RC of the rotor,
The outer periphery center of the first portion and the outer periphery center of the second portion are located on opposite sides of the rotation center RC of the rotor as viewed from the side,
Compressor.
The compression mechanism includes a piston,
The second part is between the first part and the piston;
The outer peripheral center of the first part and the central axis PC of the piston are located on the same side with respect to the rotation center RC of the rotor as viewed from the side,
The outer peripheral center of the second part is located on the opposite side of the outer peripheral center of the first part and the central axis PC of the piston across the rotation center RC of the rotor as viewed from the side.
The compressor according to claim 1.