Compressor motor and compressor equipped with same

There is provided a compressor motor in which a teeth member and a yoke member are bonded while inhibiting deformation of bridge portions and which is capable of decreasing drop of torque due to a leakage magnetic flux. A stator is constituted of a teeth member 26 in which inner end portions of adjacent teeth 27 are continuous in a bridge portion and on which wires are wounded, and a yoke member 28 bonded to an outer side of the teeth member to form a magnetic path, the yoke member includes press-fitting concave regions 32 which are opened inwardly and into which outer end portions of the teeth are press-fitted, and inner side surfaces 32A of the press-fitting concave regions which face each other possess projecting shapes, respectively, and both side surfaces 27B of each of the outer end portions of the teeth are formed in a recessed shape which matches the shape of the inner side surfaces of the press-fitting concave regions.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a U.S. National Stage Patent Application under 37 U.S.C. § 371 of International Patent Application No. PCT/JP2016/086377, filed Dec. 7, 2016, which claims the benefit of Japanese Patent Application No. JP 2015-253454, filed Dec. 25, 2015, the disclosures of each of which are incorporated herein by reference in their entirety.

TECHNICAL FIELD

The present invention relates to a compressor motor stored in a container of a compressor to drive a compression element similarly stored in the container, and the compressor equipped with the motor.

BACKGROUND ART

Heretofore, a refrigerant compressing compressor for use in a refrigerating cycle has been constituted by storing, in a container, a compression element of a scroll type or the like and a motor to drive this compression element (e.g., see Patent Document 1).FIG. 11shows a partial plan view of a stator core of such a conventional compressor motor (e.g., see Patent Document 2). The conventional motor is constituted of a stator100shown inFIG. 11and an unshown rotor which rotates on an inner side of the stator, and a rotary shaft to which this rotor is fixed drives the compression element.

A core101of the stator100ofFIG. 11has two divided constitutions in which a teeth member102and a yoke member103are separated, and in the teeth member102, inner end portions (tip portions)104A and104A of respective adjacent teeth104and104are continuous with each other in a bridge portion105. Consequently, slots106of the teeth member102open outwardly and have a closed shape in a central direction. Furthermore, unshown wires are attached to the respective teeth104from the outside, and positioned in the respective slots106. The yoke member103is bonded to outer ends of the teeth104of the teeth member102to which the wires are attached, thereby constituting the stator100.

Thus, in the stator100of the constitution in which the inner end portions104A of the teeth104are continuous, a density of wires is increased to be larger than that in a motor on which a wire is directly wound from a nozzle inserted into a clearance of each of teeth inner end portions, and improvement of performance is achievable. Furthermore, the inner end portions104A of the teeth104are continuous, thereby improving their rigidities, and hence, there is the advantage that an amount of deformation of the core101of the stator100due to a reactive force which accompanies the rotation of the rotor is also decreased and that generation of vibration is also inhibited.

CITATION LIST

Patent Documents

Patent Document 1: Japanese Patent Application Publication No. 2011-64099

SUMMARY OF THE INVENTION

Problems to be Solved by the Invention

However, due to continuous inner end portions104A of teeth104, a magnetic flux which originally has to pass a magnetic path passing through a yoke member103takes a shortcut through bridge portions105, and a so-called leakage magnetic flux is generated. Furthermore, due to this leakage magnetic flux, drop of torque occurs, and hence, it becomes necessary to decrease the leakage magnetic flux by narrowing a width of each of the bridge portions105in a radial direction as shown inFIG. 11.

On the other hand, the teeth member102and the yoke member103are bonded by press-fitting outer end portions of the teeth104of the teeth member102into a plurality of (the same number as that of the teeth104) press-fitting concave regions108formed in the yoke member103, and pressing the teeth member102with the yoke member103from the outside (a circumferential side). Therefore, during this press-fitting, a fastening load Fr is applied to the teeth104from the outside toward an inward direction (a central direction) as shown by a thin arrow inFIG. 11.

Furthermore, stress of a bend moment generated by an electromagnetic force F (shown by a bold arrow inFIG. 11) of a rotating rotor is also applied to the teeth104. Therefore, when the width of each of the bridge portions105of the teeth104is narrowed to decrease the leakage magnetic flux as described above and its strength deteriorates, there is the problem that the bridge portions105are deformed due to stress of the fastening load Fr and the stress of the bend moment generated by the electromagnetic force F.

The present invention has been developed to solve such conventional technical problems, and there are provided a compressor motor which has a structure where a teeth member and a yoke member are bonded while inhibiting deformation of bridge portions and which is capable of decreasing drop of torque due to a leakage magnetic flux, and a compressor in which the compressor motor is used.

Means for Solving the Problems

To solve the above problems, a compressor motor of the present invention is stored in a container to drive a compression element, includes a stator, and a rotor which is fixed to a rotary shaft to drive the compression element and which rotates on an inner side of the stator, and is characterized in that the stator is constituted of a teeth member in which inner end portions of adjacent teeth are continuous in a bridge portion and on which wires are wounded, and a yoke member bonded to an outer side of the teeth member to form a magnetic path, this yoke member includes press-fitting concave regions which are opened inwardly and into which outer end portions of the teeth are press-fitted, and inner side surfaces of this press-fitting concave region which face each other possesses projecting shapes, respectively, and both side surfaces of each of the outer end portions of the teeth are formed in a recessed shape which matches the shape of the inner side surfaces of the press-fitting concave regions.

The compressor motor of a particular embodiment is characterized in that in the above invention, projecting portions are formed in the inner side surfaces of the press-fitting concave region which face each other, respectively, recessed portions are formed at positions which match the respective projecting portions of the press-fitting concave regions, in both the side surfaces of each of the outer end portions of the teeth, respectively, and the projecting portions are press-fitted into the recessed portions, respectively.

The compressor motor of a particular embodiment is characterized in that in the above invention, the respective projecting portions formed in the inner side surfaces of the press-fitting concave region which face each other have a wedge shape, and the respective recessed portions formed in both the side surfaces of each of the outer end portions of the teeth have a V-shape which matches the wedge shape of the projecting portions of the press-fitting concave regions.

The compressor motor of a particular embodiment is characterized in that in the above invention, when a dimension from an outer end face of each of the teeth to an apex of the V-shape of the recessed portion in a direction parallel to a radial direction is defined as a, a dimension from a side surface of the teeth to the apex of the V-shape of the recessed portion in a width direction of the teeth is defined as b, a width dimension of the teeth is defined as B, a dimension from the outer end face of the teeth to a position of an opening of the press-fitting concave region in the direction parallel to the radial direction is defined as e, yield stress of the teeth member is defined as σy, and contact stress to be applied to the teeth when the outer end portion of the teeth is press-fitted into the press-fitting concave region is defined as σr, a value of a is set to a range of σr·B/(σy−σr)≤a≤{(B−2b)/B}2·e.

A compressor of a particular embodiment is characterized by including a constitution in which the motor of the above respective inventions and the compression element are stored in the container.

Advantageous Effect of the Invention

According to the present invention, a compressor motor stored in a container to drive a compression element includes a stator, and a rotor which is fixed to a rotary shaft to drive the compression element and which rotates on an inner side of the stator. The stator is constituted of a teeth member in which inner end portions of adjacent teeth are continuous in a bridge portion and on which wires are wounded, and a yoke member bonded to an outer side of this teeth member to form a magnetic path. Consequently, a density of the wires can be increased to achieve improvement of performance. Furthermore, the inner end portions of the teeth are continuous in the bridge portions, and their rigidities improve. Therefore, an amount of deformation of the stator due to a reactive force which accompanies the rotation of the rotor decreases, and generation of vibration is also inhibited.

In particular, the yoke member includes press-fitting concave regions which are opened inwardly and into which outer end portions of the teeth are press-fitted, and inner side surfaces of this press-fitting concave region which face each other possess projecting shapes, respectively, and both side surfaces of each of the outer end portions of the teeth are formed in a recessed shape which matches the shape of the inner side surfaces of the press-fitting concave regions. Consequently, outwardly positioned surfaces of inner surfaces of recessed portions of the recessed shape can receive a fastening load from the outside which is generated in press-fitting the teeth of the teeth member into the press-fitting concave regions of the yoke member.

Consequently, it is possible to decrease stress to be applied to the bridge portions in bonding the teeth member and the yoke member, and hence, even when a width of each bridge portion is narrowed, its deformation can be inhibited, a magnetic flux is hard to pass the bridge portions, leakage of the magnetic flux which takes a shortcut between the inner end portions of each teeth can remarkably be decreased, and it is possible to effectively inhibit drop of torque due to the leakage magnetic flux.

Furthermore, as in a particular embodiment, projecting portions are formed in the inner side surfaces of the press-fitting concave region which face each other, respectively, recessed portions are formed at positions which match the respective projecting portions of the press-fitting concave regions, in both the side surfaces of each of the outer end portions of the teeth, respectively, and the projecting portions are press-fitted into the recessed portions, respectively. Consequently, the outwardly positioned surface of the inner surface of each recessed portion receives the fastening load generated in bonding the teeth member and the yoke member, so that it is possible to effectively decrease the stress to be applied to the bridge portions.

In particular, as in a particular embodiment, the respective projecting portions formed in the inner side surfaces of the press-fitting concave region which face each other have a wedge shape, and the respective recessed portions formed in both the side surfaces of each of the outer end portions of the teeth have a V-shape which matches the wedge shape of the projecting portions of the press-fitting concave regions. Consequently, the teeth of the teeth member can easily be press-fitted into the press-fitting concave regions of the yoke member, whereas the projecting portions can effectively receive the fastening load.

In this case, as in a particular embodiment, when a dimension from an outer end face of each of the teeth to an apex of the V-shape of the recessed portion in a direction parallel to a radial direction is defined as a, a dimension from a side surface of the teeth to the apex of the V-shape of the recessed portion in a width direction of the teeth is defined as b, a width dimension of the teeth is defined as B, a dimension from the outer end face of the teeth to a position of an opening of the press-fitting concave region in the direction parallel to the radial direction is defined as e, yield stress of the teeth member is defined as σy, and contact stress to be applied to the teeth when the outer end portion of the teeth is press-fitted into the press-fitting concave region is defined as σr, a value of a is set to a range of σr·B/(σy−σr)≤a. Consequently, it is possible to prevent the disadvantage that the outwardly positioned surface of the inner surface of the V-shaped recessed portion is crushed due to the fastening load and that the stress to be applied to the bridge portions of the inner end portions of the teeth increases.

Furthermore, when the value of a is set to the range of a≤{(B−2b)/B}2·e, it is possible to prevent deterioration of strength of the teeth themselves which is caused by forming the outer end portions of the teeth in the recessed shape, it is possible to also counteract a bend moment generated by an electromagnetic force of the rotating rotor without hindrance, and in general, it is possible to decrease deformation of the bridge portions due to both of stress of the fastening load generated in bonding the teeth member and the yoke member and stress of the bend moment generated by the electromagnetic force of the rotating rotor.

Furthermore, as in a particular embodiment, a compressor includes a constitution in which the motor of the above respective inventions and the compression element are stored in the container, so that it is possible to obtain a small compressor having less vibration and high performance.

MODE FOR CARRYING OUT THE INVENTION

Hereinafter, description will be made in detail as to embodiments of the present invention.

InFIG. 1, a compressor1of the embodiment is a scroll compressor in which a scroll compression element3and a motor4of the present invention are stored in a container2. The scroll compression element3includes a fixed scroll6fixed to the container2, and a movable scroll7revolved by a rotary shaft8of the motor4without rotating to the fixed scroll6, and a spiral lap11formed in the fixed scroll6and a spiral lap12formed in the movable scroll7are arranged to mesh with each other.

A refrigerant is introduced into the container2from an unshown refrigerant introduction passage, and sucked into a compressing chamber constituted between both the laps11and12from the outside. This compressing chamber narrows toward its center due to a revolving motion of the movable scroll7, and hence, the sucked refrigerant is compressed and discharged from a central portion through a discharge chamber14and an unshown refrigerant discharge passage. Furthermore, a low pressure is provided in the container2, and hence, the refrigerant also passes the motor4, so that the motor4is cooled with this refrigerant.

Next, description will be made as to the motor4of the present invention. The motor4of the embodiment is a permanent magnet synchronous motor, and is constituted of a stator21including a core22and wires23, and a built-in magnet type of rotor24(formed by laminating a plurality of electromagnetic steel plates) which is fixed to the rotary shaft8and which rotates on an inner side of the stator21.

The core22of the stator21has two divided constitutions in which a teeth member26(an inner core) having a plurality of (the number corresponding to the number of poles, e.g., twelve in the embodiment) teeth27and a yoke member28(an outer core) bonded to an outer side of the teeth member26to form a magnetic path are separated, and inner end portions (tip portions)27A and27A of the adjacent teeth27and27of the teeth member26are continuous with each other in a bridge portion29. Consequently, a slot31between the respective teeth27of the teeth member26opens outwardly, and has a closed shape in its central direction.

Each of the teeth member26and the yoke member28has a constitution in which a plurality of electromagnetic steel plates (the electromagnetic steel plates made of the same material) are laminated and bonded. Furthermore, in an inner side surface of the yoke member28, the same number of press-fitting concave regions32as the number of the teeth27of the teeth member26are formed. Each press-fitting concave region32is opened inwardly and end portions thereof are also opened in an axial direction of the rotary shaft8. Additionally, inner side surfaces32A and32A of the press-fitting concave region32which face each other possess wedged projecting shapes, respectively, as shown inFIG. 7, and projecting portions35and35having a wedge shape are formed therein.

On the other hand, both side surfaces27B and27B of an outer end portion of each teeth27which is to be press-fitted into the press-fitting concave region32are formed into a recessed shape of a V-shape which matches a projecting shape of the inner side surfaces32A and32A of the press-fitting concave region32, and V-shaped recessed portions30and30are formed in the side surfaces, respectively. Furthermore, the recessed portions30and30are formed at positions which match the projecting portions35and35, when the teeth27is press-fitted into the press-fitting concave region32. It is to be noted that description will be made later in detail as to a shape of the projecting portion35or the recessed portion30. Additionally, the wire23is beforehand wound on a bobbin33constituted of an insulator, and in the bobbin33, there is formed an attaching hole34into which the teeth27of the teeth member26is to be inserted.

Then, when the stator21is assembled, the electromagnetic steel plates are initially laminated and bonded, thereby constituting the teeth member26and the yoke member28. Furthermore, the wire23is wound on the bobbin33, and twelve bobbins are prepared. Next, the teeth27of the teeth member26are inserted into the attaching holes34of the respective bobbins33on which the wires23are wound so that the bobbins33are attached to all the teeth27from the outside (twelve bobbins in total are attached).

In this way, the wires23are wound on the teeth member26. Next, the yoke member28is bonded to the outer side of the teeth member26provided with the wires23. In this case, the outer end portions of the respective teeth27of the teeth member26are press-fitted into the respective press-fitting concave regions32of the yoke member28in the axial direction (from the upside inFIG. 2), thereby integrating the teeth member26and the yoke member28(FIG.7). It is to be noted that the wires23of the respective bobbins33are arranged to constitute a predetermined electric circuit. Furthermore, in and afterFIG. 4, the drawing of the bobbins33and the wires23is omitted.

Thus, in the stator21, the inner end portions (the tip portions)27A of the teeth27are continuous, and the wires23are attached to the outwardly opened slots31from the outside, and hence, a density of the wires is increased to be larger than that in a motor on which a wire is directly wound from a nozzle inserted into a clearance of each of teeth tips, and improvement of performance is achievable.

Furthermore, in the teeth member26, the inner end portions (the tip portions)27A of the respective teeth27are continuous in the bridge portions29, thereby improving their rigidities, and hence, there is the advantage that an amount of deformation of the core22of the stator21due to a reactive force generated from an electromagnetic force which accompanies the rotation of the rotor24is also decreased and that generation of vibration is also inhibited. However, drop of torque due to a leakage magnetic flux which passes a continuous portion of each teeth27becomes a problem.

To eliminate such a problem, in the embodiment, the bridge portions29are formed so that a width of each bridge portion in a radial direction is narrower than that of the inner end portion27A of the teeth27and the bridge portion has a predetermined length dimension in a circumferential direction (FIG. 6). Consequently, a magnetic flux is hard to pass the bridge portions29, leakage of the magnetic flux which takes a shortcut between the inner end portions27A of the teeth27remarkably decreases, and hence, the drop of the torque due to the leakage magnetic flux is effectively inhibited.

Next, description will be made in detail as to shapes of the projecting portions35and35formed in the inner side surfaces32A and32A of the press-fitting concave region32of the yoke member28which face each other, and the recessed portions30and30formed in both the side surfaces27B and27B of the outer end portion of the teeth27to be press-fitted into the press-fitting concave region32.

As described above, the wedge-shaped projecting portions35and35are formed in the inner side surfaces32A and32A of the press-fitting concave region32of the yoke member28which face each other, respectively, and the V-shaped recessed portions30and30are formed in both the side surfaces27B and27B of the outer end portion of the teeth27of the teeth member26which is to be press-fitted into the press-fitting concave region32, respectively. Furthermore, the recessed portions30and30are formed at the positions which match the projecting portions35and35when the teeth27is press-fitted into the press-fitting concave region32, and hence, outwardly positioned surfaces P (shown inFIG. 8) of inner surfaces of the respective V-shaped recessed portions30and30can receive a fastening load Fr (shown inFIG. 8) generated in press-fitting the teeth27of the teeth member26into the press-fitting concave region32of the yoke member28and directed inwardly from the outside.

Consequently, it is possible to decrease stress to be applied to the bridge portions29in bonding the teeth member26and the yoke member28, and hence, even when the width of each of the bridge portions29is narrowed, its deformation can be inhibited. In consequence, the width of the bridge portion29can be narrowed so that the magnetic flux is hard to pass as in the embodiment, but in accordance with the shapes or dimensions of the projecting portion35and the recessed portion30, the recessed portion30or the projecting portion35is crushed due to the fastening load Fr, and the stress to be applied to the bridge portions29cannot decrease. Furthermore, when the recessed portions30are formed and strength of the teeth member26itself therefore deteriorates, it is not possible to counteract stress of a bend moment generated by an electromagnetic force F (shown inFIG. 9) of the rotating rotor24.

To eliminate such a problem, in the present invention, the dimensions or shapes of the projecting portions35and35of the press-fitting concave region32and the recessed portions30and30of the teeth27are verified.FIG. 8schematically shows a bonded portion between the teeth member26and the yoke member28, andFIG. 9schematically shows one teeth27of the teeth member26(the bridge portion29is omitted) and the press-fitting concave region32. It is to be noted that the verification is performed by using, as a parameter, a dimension a from an outer end face27C of the teeth27to an apex30A of the V-shape of the recessed portion30in a direction parallel to the radial direction and setting this dimension a to a proper range. Furthermore,FIG. 9shows that the outer end portion of the teeth27is disposed away from the press-fitting concave region32, but in actual, both the teeth and the region are brought into contact under pressure with each other with a predetermined overlapping margin.

(5-1) Range to Prevent Crush of Outwardly Positioned Surfaces P of Inner Surfaces of V-Shaped Recessed Portions30and30

Initially, inFIG. 8, a is the dimension from the outer end face27C of the teeth27to the apex30A of the V-shape of the recessed portion30in the direction parallel to the radial direction, b is a dimension from a side surface of the teeth27to the apex30A of the V-shape of the recessed portion30in a width direction of the teeth27, e is a dimension from the outer end face27C of the teeth27to a position of an opening of the press-fitting concave region32in the direction parallel to the radial direction, θ is an angle formed by the outwardly positioned surface P of the inner surface of the V-shaped recessed portion30and a line in the circumferential direction, A is a width dimension of the surface P, B is a width dimension of the teeth27, L is a laminate thickness of the teeth member26and the yoke member28(an overall thickness dimension of the laminated electromagnetic steel plates), and Fr is the fastening load to be applied to the teeth27when the outer end portion of the teeth27of the teeth member26is press-fitted into the press-fitting concave region32of the yoke member28.

Furthermore, when contact stress to be applied to the teeth27in the press-fitting is defined as σr, a contact reactive force is defined as Rr, contact stress of the surface P is defined as σa, and yield stress of the electromagnetic steel plate (a material) constituting the teeth member26and the yoke member28is defined as σy, the fastening load Fr is represented by Equation (I) mentioned below, and the contact stress σa of the surface P is represented by Equation (II) mentioned below.
Fr=σr·B·L . . .(I)
σa=Rr/(A·L)+σr . . .(II)

Then, when the contact stress σa of the surface P is not more than the yield stress σy, the outwardly positioned surface P of the inner surface of the V-shaped recessed portion30is not crushed by the fastening load Fr. Therefore, when a right side of Equation (III) mentioned above is substituted into a left side of this relation (σa≤σy) and a is derived, the following equation is formed.
σr·B/(σy−σr)≤a . . .(IV)
That is, it is seen that when the dimension a is set to the range of Equation (IV) mentioned above, the outwardly positioned surfaces P of the inner surfaces of the V-shaped recessed portions30of the teeth27are not crushed by the fastening load Fr, and there is prevented the disadvantage that the stress to be applied to the bridge portions29of the inner end portions27A of the teeth27increases.

(5-2) Range to prevent Strength Deterioration of Teeth Member26

Next, inFIG. 9, 1 is a dimension from the inner end portion27A of the teeth27to the opening of the press-fitting concave region32(the inner side surface of the yoke member28), and the other dimensions are similar to those ofFIG. 8. When the bend moment to be applied to the teeth27at a position of the dimension a due to the electromagnetic force F of the rotating rotor24(shown inFIG. 9) is Ma, a bend moment to be applied to the teeth27at a position of the dimension e is Me, surface stress to be applied to the teeth27at the position of the dimension a is σab, and surface stress to be applied to the teeth27at the position of the dimension e is σeb, the moment Ma, the moment Me, the surface stress σab and the surface stress σeb are represented by Equations (V) to (VIII) mentioned below, respectively.
Ma=F·(1/e)·a. . . (V)
Me=F·1 . . . (VI)
σab=6Ma/{L·(B−2b)2} . . . (VII)
σeb=6Me/(L·B2) . . . (VIII)

When the recessed portion30is not formed, the bend moment to be applied to the teeth27is maximized at the position of the dimension e (denoted with Mmax in a diagram shown on the right side ofFIG. 9). Therefore, when the surface stress σab of the teeth27at the position of the dimension a is not more than the surface stress σeb of the teeth27at the position of the dimension e, there is eliminated the problem that the strength of the teeth member26itself deteriorates due to the formation of the recessed portion30. Consequently, when Equation (VII) mentioned above is substituted into a left side of this relation (σab≤σeb) and Equation (VIII) mentioned above is substituted into a right side thereof to derive a, the following equation is formed.
a≤{(B−2b)/B}2·e. . . (IX)
That is, it is seen that when the dimension a is set to the above range of Equation (IX) mentioned above, there is prevented the deterioration of the strength of the teeth27itself due to the formation of the recessed portions30in the outer end portions of the teeth27.

(5-3) Proper Range of Dimension a

Therefore, it is seen from Equation (IV) and Equation (IX) mentioned above that the Equation (X) mentioned above indicates the proper range of the dimension a.
σr·B/(σy−σr)≤a≤{(B−2b)/B}2·e . . .(X)

FIG. 10shows this behavior. It is to be noted that the ordinate on the right side ofFIG. 10indicates a ratio (a stress ratio: σab/σeb) of the surface stress σab to the surface stress σeb. When the ratio is 1 or less, a relation (σab≤σeb) is satisfied. Furthermore, the ordinate on the left side indicates the contact stress σa, and the stress may be not more than yield stress σy. Furthermore, the abscissa indicates the position of the apex30A of the V-shape (a value of the dimension a).

In the embodiment, the dimension a is set to this range of Equation (X). Consequently, it is possible to prevent the disadvantage that the outwardly positioned surfaces P of the inner surfaces of the V-shaped recessed portions30are crushed and that the stress to be applied to the bridge portions29of the inner end portions27A of the teeth27increases. Furthermore, it is possible to prevent the deterioration of the strength of the teeth27themselves which is caused by forming the recessed portions30in the outer end portions of the teeth27, and it is possible to counteract the bend moment generated by the electromagnetic force F of the rotating rotor24without hindrance. In general, it is possible to decrease the deformation of the bridge portions29due to both of the stress of the fastening load Fr generated in bonding the teeth member26and the yoke member28and the stress of the bend moment generated by the electromagnetic force F of the rotating rotor24.

It is to be noted that the recessed portions30formed in the teeth27of the teeth member26have a shape which matches the projecting portions35formed in the press-fitting concave regions32of the yoke member28, and hence, the dimension a shown inFIG. 8andFIG. 9of the above embodiment can be replaced with a dimension from an inner bottom surface of the press-fitting concave region32(the surface which matches the outer end face27C of the teeth27) to an apex of the wedge shape of the projecting portion35in a direction parallel to the radial direction, the dimension b can be replaced with a dimension from the inner side surface32A of the press-fitting concave region32to the apex of the wedge shape of the projecting portion35in a width direction of the press-fitting concave region32, the dimension e can be replaced with a depth dimension of the press-fitting concave region32(a dimension of the inner side surface32A in a thickness direction of the yoke member28), the angle θ can be replaced with an angle formed by an outer surface of the projecting portion35and a line in a circumferential direction, A can be replaced with a width dimension of the outer surface of the projecting portion35, the dimension B can be replaced with a width dimension of the inner bottom surface of the press-fitting concave region32, σr can be replaced with contact stress to be applied to the press-fitting concave region32in the press-fitting, and σa can be replaced with contact stress of the outer surface of the projecting portion35. Furthermore, the teeth member26and the yoke member28are made of the same material, and hence, the crush due to the fastening load occurs not only in the teeth27but also in the press-fitting concave regions32of the yoke member28.

Additionally, in the embodiment, it has been described that the projecting portions35have the wedge shape, but this does not restrict the inventions of other embodiments, and the projecting portions may have a circular shape or a rectangular shape. Furthermore, in the embodiment, the present invention is employed in the scroll compressor, but this does not restrict the invention, and the motor4of the present invention is suitable for various compressors including a rotary compressor.

DESCRIPTION OF REFERENCE NUMERALS

1compressor2container3scroll compression element4motor8rotary shaft21stator22core23wire24rotor26teeth member27teeth27A inner end portion27B side surface27C outer end face28yoke member29bridge portion30recessed portion30A apex of V-shape31slot32press-fitting concave region32A inner side surface35projecting portionP outwardly positioned surface of an inner surface of the V-shaped recessed portion