KR102060476B1 - Motor operated compressor - Google Patents

Abstract

According to the present invention, an electric compressor includes: a first scroll installed on one side of a driving motor, penetrated by a rotary shaft in an axial direction to be eccentrically combined, and rotated by the rotary shaft; a second scroll forming a compression chamber together with the first scroll, and supporting the rotary shaft in a radial direction; a main housing combined with the second scroll, and comprising a motor chamber combined with the driving motor to form an inhalation space, an opening end formed on one side of the motor chamber, a frame part formed on the other side of the motor chamber to support the second scroll in an axial direction, and a first shafting part formed in the frame part to be penetrated by the rotary shaft to be supported in a radial direction; and an inverter housing storing an inverter element electrically connected with the driving motor, and combined with the opening end of the main housing to seal the motor chamber. Between the opening end of the main housing and a sealing surface part of the inverter housing, which faces the opening end of the main housing, a combination part can be installed to combine the opening end of the main housing with the sealing surface part of the inverter housing.

Description

Electric Compressor {MOTOR OPERATED COMPRESSOR}

The present invention relates to an electric compressor.

As the electric compressor, a scroll compression type electric compressor suitable for high compression ratio operation is widely known. In the scroll type electric compressor (hereinafter, abbreviated as “electric compressor”), an electric motor drive unit is installed in a sealed casing, and a compression unit consisting of a fixed scroll and a rotating scroll is installed on one side of the electric motor. Compression unit is connected to the rotating shaft is configured to transmit the rotational force of the transmission unit to the compression unit.

Such a motor-driven compressor is provided with an inverter module, which may be installed on the radial side of the casing or on the axial side. Recently, in consideration of heat dissipation of the inverter module, an electric compressor for installing the inverter module on the axial side of the casing has been introduced. Prior art [Korean Patent Publication No. 10-2016-0104398 (published: 2016.09.05)] shows an example in which the inverter module is installed on the axial side of the compressor casing.

In the electric compressor according to the related art, one end of the housing 200 is formed in a structure in which the other end is blocked, and the compression part including the center head 210 forming the main frame is formed in one end of the housing 200, and an inverter module is formed in the other end of the block. Inverter casings 130 are provided, respectively. As a result, the transmission portion and the compression portion are inserted into and coupled to the blocked portion from the opening side of the housing in order.

However, in the conventional electric compressor as described above, the coupling portion 200a (unsigned) is formed on the outer circumferential surface of the housing 200 and the rear head 300 or the housing 200 and the inverter casing 130, respectively, and both sides are fastened. By fastening the protrusions with the bolts 30, the outer diameter of the compressor is increased so that the weight of the compressor is increased as well as a large space is required to install the compressor.

In addition, in the conventional electric compressor, the gasket 270 is installed between the housing 200 and the rear head 300 covering the housing, but the gasket is formed in an annular plate shape, whereby the sealing area is narrowed. In order to seal the inner space of the housing, there is a problem in that the thickness of the housing or the rear head needs to be increased or the fastening force must be increased.

In addition, in the conventional motor-driven compressor, the coupling surface between the housing 200 and the member coupled to the housing is formed flat, which causes a problem that it is difficult to assemble the housing and the member coupled to the housing accurately.

Prior art: Korean Patent Publication No. 10-2016-0104398 (Published: 2016.09.05)

An object of the present invention is to provide an electric compressor that can be combined with the main housing to increase the sealing area to the inner space of the main housing by expanding the sealing area between the member and the sealing member for sealing the inner space of the main housing. .

In addition, another object of the present invention is to provide an electric compressor that can suppress the increase in weight or size of the compressor by simplifying the fastening structure with the member coupled to the main housing.

In addition, another object of the present invention is to provide an electric compressor that forms a stepped surface in the inverter housing coupled to the main housing to match the assembly position of the main housing and the inverter housing.

In order to achieve the object of the present invention, the motor housing is provided with a main housing; A driving motor fixed to the inside of the main housing; A fixed scroll coupled to the main housing at an outside of the main housing; A rotating scroll which engages with the fixed scroll outside the main housing to form a compression chamber; And an inverter housing coupled to the main housing to seal the motor compartment.

In this case, the main housing may be integrally formed with a frame portion in which the pivoting scroll is supported in the axial direction.

The inverter housing may include a sealing protrusion formed to be inserted into the main housing, and a sealing member may be provided between an outer circumferential surface of the sealing protrusion and an inner circumferential surface of the main housing.

In addition, to achieve the object of the present invention, a drive motor having a stator and a rotor; A rotating shaft coupled to the rotor; A first scroll provided on one side of the drive motor, the rotation shaft penetrating axially and eccentrically coupled to the pivot by the rotation shaft; A second scroll coupled to the first scroll to form a compression chamber together with the first scroll, and a rotation shaft penetrating the first scroll to be rotatably inserted and supporting the rotation shaft in a radial direction; A motor chamber coupled to the second scroll from the outside of the second scroll and the driving motor is coupled to form a suction space is formed, one side of the motor chamber is an open end, and the other side of the motor chamber is A main housing in which a second scroll is supported in an axial direction, respectively, and a main housing in which the first bearing is formed so that the rotating shaft penetrates and is supported in a radial direction; And an inverter housing accommodating an inverter element electrically connected to the driving motor, the inverter housing being coupled to the opening end of the main housing to seal the motor compartment. The opening end of the main housing and the opening end of the main housing. An electric compressor may be provided between the opposing sealing surface portions of the inverter housing, the fastening portion coupling the open end of the main housing and the sealing surface portion of the inverter housing.

Here, the fastening part may be formed in a plurality of rivets extending in the axial direction from the open end of the main housing at predetermined intervals along the circumferential direction, the plurality of rivets may be coupled through the inverter housing. .

The fastening part may be formed of a plurality of rivets axially pressed into the opening end of the main housing and formed at predetermined intervals along the circumferential direction, and the plurality of rivets may be coupled through the inverter housing. .

The fastening part may be formed of a material different from that of the main housing.

The fastening part may be formed of a bolt which penetrates the opening of the main housing through the inverter housing.

The fastening part may be formed of a material different from that of the main housing.

A sealing protrusion protruding in an annular shape may be formed at one side of the sealing surface portion, and the sealing protrusion may be inserted into an opening end of the main housing.

In addition, a sealing member may be provided between the main housing and the inverter housing.

The sealing member may include a first sealing part disposed between an open end of the main housing and a sealing surface portion of the inverter housing and having a plurality of holes through the fastening part; And a second sealing part disposed between an inner circumferential surface of the main housing and an outer circumferential surface of a sealing protrusion of the inverter housing.

The first sealing part and the second sealing part may be integrally formed.

The second sealing part may be separated from the first sealing part and may have a ring shape inserted into an inner circumferential surface of the main housing or an outer circumferential surface of a sealing protrusion of the inverter housing.

The sealing member may have a ring shape located between an inner circumferential surface of the main housing and an outer circumferential surface of a sealing protrusion of the inverter housing.

In addition, to achieve the object of the present invention, a drive motor having a stator and a rotor; A rotating shaft coupled to the rotor; A first scroll provided on one side of the drive motor, the rotation shaft penetrating axially and eccentrically coupled to the pivot by the rotation shaft; A second scroll coupled to the first scroll to form a compression chamber together with the first scroll, and a rotation shaft penetrating the first scroll to be rotatably inserted and supporting the rotation shaft in a radial direction; A motor chamber coupled to the second scroll from the outside of the second scroll and the driving motor is coupled to form a suction space is formed, one side of the motor chamber is an open end, and the other side of the motor chamber is A main housing in which a second scroll is supported in an axial direction, respectively, and a main housing in which the first bearing is formed so that the rotating shaft penetrates and is supported in a radial direction; And an inverter housing accommodating an inverter element electrically connected to the driving motor, the inverter housing being coupled to the opening end of the main housing to seal the motor compartment. The inverter housing of the inverter housing facing the opening end of the main housing. A sealing protrusion protruding in an annular shape and inserted into an opening end of the main housing is formed at one side of the sealing surface part, and a sealing member is provided between the opening end of the main housing and the sealing surface part of the inverter housing. Compressors may be provided.

Here, the sealing member may include a first sealing part located between the open end of the main housing and the sealing surface of the inverter housing; And a second sealing part disposed between an inner circumferential surface of the main housing and an outer circumferential surface of a sealing protrusion of the inverter housing.

In addition, a plurality of rivet parts are formed in the opening end of the main housing in the axial direction at predetermined intervals along the circumferential direction, and a plurality of rivet through holes are formed in the first sealing part to penetrate the rivet parts. A plurality of rivet holes may be formed in the sealing surface portion of the inverter housing so that the plurality of rivet portions penetrate through the sealing surface portion.

The motor-driven compressor according to the present invention penetrates the first end of the main housing and the sealing surface portion of the inverter housing in contact with each other by rivets or bolts, thereby eliminating the fastening protrusions on the outer circumferential surfaces of the main housing and the inverter housing, respectively. It is possible to fasten the sealing surface portion of the first stage and the inverter housing. Accordingly, the outer diameter of the compressor is reduced compared to fastening both housings by forming fastening protrusions on the outer peripheral surfaces of the main housing and the inverter housing, thereby reducing the weight of the compressor and reducing the space required for installing the compressor. .

In the electric compressor according to the present invention, a sealing member made of a gasket is installed between the main housing and the inverter housing, and the sealing member includes a first sealing portion and a second sealing portion to seal the outer circumferential surfaces of the sealing surface portion and the sealing protrusion, respectively. Done. Accordingly, the sealing area is increased without increasing the thickness of the main housing and the inverter housing, so that the motor chamber can be more effectively sealed.

In addition, the motor-driven compressor according to the present invention can easily match the assembly position of the inverter housing when assembling the inverter housing to the main housing by forming a sealing protrusion on the inverter housing coupled to the main housing. Accordingly, the assembling work of the main housing and the inverter housing can be easily and accurately performed.

In addition, the motor-driven compressor according to the present invention, by integrally forming the frame portion in the main housing, it is possible to easily form the main frame to simplify the manufacturing process of the compressor.

In addition, the motor-driven compressor according to the present invention, by opening one end of the main housing to which the inverter housing is coupled to insert the drive motor, it is possible to reduce the insertion depth of the drive motor and thereby facilitate assembly of the drive motor. Can be.

1 is a perspective view showing the compressor module and the inverter module separated from the electric compressor according to the present embodiment;
2 is a cross-sectional view showing the interior of the electric compressor according to FIG. 1;
3 is a cross-sectional view of the main housing in the motor-driven compressor according to FIG.
4 is a front view of the main housing in FIG. 3 seen from the rear side;
5 is a cross-sectional view showing a rotating shaft and a bearing for supporting the rotating shaft according to the embodiment;
6 is a cross-sectional view of a second scroll according to the present embodiment;
7 is a front view showing the second scroll according to FIG. 6 from the front side;
FIG. 8 is a plan view illustrating a coupling relationship between a non-involute shape swing wrap and a fixed wrap in the electric compressor according to the present embodiment; FIG.
9 is an enlarged cross-sectional view of a coupling portion of the main housing and the inverter housing in FIG.
10 is a cross-sectional view showing another embodiment of the rivet coupling structure in FIG.
11 and 14 are cross-sectional views illustrating other embodiments of a coupling structure of a main housing and an inverter housing in FIG. 9.

Hereinafter, the electric compressor according to the present invention will be described in detail based on the embodiment shown in the accompanying drawings.

1 is a perspective view showing the compressor module and the inverter module separately from the motor-driven compressor according to the present embodiment, and FIG. 2 is a cross-sectional view showing the inside of the motor-driven compressor according to FIG. 1.

As shown therein, the scroll-type electric compressor (hereinafter, abbreviated to the electric compressor) according to the present embodiment is coupled to the compressor module 101 for compressing the refrigerant and the compressor module 101 in front of the compressor. Inverter module 201 may be configured to control the driving of module 101. The compressor module 101 and the inverter module 201 may be assembled in succession or may be assembled after being fabricated independently of each other. Although the present embodiment will be described using the latter as a representative example, the compressor module and the inverter module may be independently manufactured in the form of a mixture of the former and the latter, but may be continuously assembled.

The compressor module 101 is a main housing 110 in which the inlet port 111 is formed so that the inner space forms the motor chamber S1 and communicates with the motor chamber, and the transmission unit fixed to the motor chamber S1 of the main housing 110. Compression unit 105 and compression unit 105 provided on one side of the drive motor 120 outside the main motor 110 and the main housing 110 to compress the refrigerant using the rotational force of the drive motor 120. It is coupled to the other side of the includes a rear housing 160 to form an oil separation chamber (S2).

As the main housing 110 is disposed in the transverse direction with respect to the ground, the drive motor 120 and the compression unit 105 are arranged along the transverse direction, and for convenience, designate the left side of FIG. 2 as the front side and the right side as the rear side. Will be explained.

The main housing 110 is formed in a cup cross-sectional shape in which the front end is opened and the rear end is partially blocked. Inverted front end of the main housing 110, the inverter housing 210 to be described later is coupled and sealed, the closed rear end of the main housing 110 frame 112 for supporting the compression section 105 integrally Is formed extending. In the frame portion 112 of the main housing 110, a first bearing portion 113 through which the main bearing portion 132 of the rotating shaft 130 to be described later is rotatably supported is formed in a cylindrical shape.

A first bearing 171 made of a bush bearing is inserted into and coupled to the first bearing portion 113, and an inner circumferential surface of the first bearing portion 113 is spaced apart from the main bearing portion 132 of the rotation shaft 130 to be described later. The back pressure chamber S3 may communicate with the motor chamber S1. As the intake port 111 to which the suction pipe (not shown) is connected near the front end of the main housing 110 is formed, the motor chamber S1 of the present embodiment forms a kind of suction space. Therefore, the electric compressor according to the present embodiment forms a low pressure compressor as the refrigerant is sucked into the compression unit through the inner space of the main housing forming the motor compartment.

The main housing according to the present embodiment integrally forms the frame portion as described above. Accordingly, by eliminating the process of assembling the frame to the main housing separately, the assembly maneuverability can be reduced and assembly of the drive motor can be improved.

FIG. 3 is a cross-sectional view of the main housing in a side view of the electric compressor according to FIG. 2, and FIG. 4 is a front view of the main housing in FIG. 3.

As shown therein, the axis center Ob1 of the first bearing portion 113 is formed to coincide with the axis center Om of the driving motor 120. To this end, the center of the outer diameter of the frame portion 112 and the center of the inner diameter (that is, the center of the first bearing portion) may be formed to coincide.

However, the shaft center Ob1 of the first bearing part 113 coincides with the shaft center Om of the driving motor 120, but the center of the outer diameter Oo of the frame part 112 and the center of the inner diameter Oi do not coincide with each other. It may be formed so as to. For example, as shown in FIGS. 3 and 4, the first protrusion 114 is formed at one radial side of the frame portion 112, and the first protrusion 114 is configured to communicate with the inside of the motor chamber S1. One flow passage 114a may be formed through. The first flow passage 114a may form a suction flow passage Fg for communicating the compression chamber V and the motor chamber S1 together with the second flow passage 154a of the second scroll 150, which will be described later.

On the other hand, the frame portion 112 is formed in such a way that the front side protrudes toward the center, that is, the first bearing portion 113 toward the drive motor 120, the rear side of the frame portion 112 is the drive motor 120 It is formed to be recessed so as to step at least two times in the direction toward). Accordingly, the rear wall of the frame portion 112 is inserted into the pivoting plate portion of the first scroll to be described later, the scroll seating groove (112a) which is supported in the axial direction, the olddaming seating groove (180) that the anti-rotation mechanism is seated ( 112b) and the balance weight receiving groove 112c in which the balance weight 138 is rotatably received are formed, respectively. The scroll seating groove 112a, the old damling seating groove 112b, and the balance weight receiving groove 112c are continuously formed to form a kind of back pressure chamber S3.

In addition, the rear end of the first bearing portion 113 protrudes in a direction toward the first scroll 140 to have a cylindrical shape, and a first bearing 171 formed of a bush bearing in the first bearing portion 113. ) Is inserted and combined. Accordingly, the rear end of the first bearing portion 113 forms the back pressure chamber S3 by forming the balance weight receiving groove 112c whose outer circumferential surface is described above.

In addition, at the rear end of the first bearing portion 113, an axial bearing surface 113a forming a thrust surface is formed together with the axial bearing protrusion 135 of the rotating shaft 130 to be described later. Here, at least one of the axial bearing surface (113a) of the first bearing portion 113 or the axial bearing surface (135a) of the axial bearing protrusion 135 provided on the rotating shaft 130 facing the axial direction The oil passage groove 113b may be formed on the bearing surface. As a result, the oil or the refrigerant in the back pressure chamber S3 moves toward the motor chamber S1 through the axial bearing surface, and the back pressure chamber S3 forms a flow pressure.

On the other hand, the drive motor 120, the stator 121 is inserted into the inner circumferential surface of the main housing 110, and the rotor is located inside the stator 121 and rotated by the interaction with the stator 121 ( 122). Rotor 122 is coupled to the rotating shaft 130 for transmitting the rotational force of the drive motor 120 to the compression unit 105 while rotating together with the rotor 122.

The stator 121 is fixed to the main housing 110 by shrinking (or hot pressing). Therefore, the stator 121 may be advantageous in reducing the insertion depth of the main housing 110 to facilitate the assembling work, and maintain the concentricity of the stator 121 in the process of shrinking the stator 121. have.

To this end, as shown in FIG. 3, the main housing 110 has a shaft of the stator 121 when the open end is referred to as the first end 110a and the end where the frame portion 112 is formed as the second end 110b. The length L1 from the center CL in the direction to the first end 110a may be shorter than the length L2 from the center CL in the axial direction of the stator 121 to the second end 110b. have. Accordingly, as described above, the insertion depth L3 for inserting the stator 121 into the motor chamber S1 of the main housing 110 may be shortened.

On the other hand, the rotating shaft 130 is coupled to the center of the rotor 122 by shrinkage (or hot pressing). The rotating shaft 130 may support both ends in the radial direction with the driving motor 120 interposed therebetween. However, as shown in this embodiment, one end of the rotation shaft 130 is a fixed end that is supported at one side of the driving motor 120, that is, two points in the radial direction from the frame part 112 and the second scroll 150, and the driving motor. The other end of the rotation shaft 130 coupled to the rotor 122 of 120 may be a free end in the radial direction.

5 is a sectional view showing a rotating shaft and a bearing for supporting the rotating shaft according to the present embodiment.

As shown therein, the rotation shaft 130 includes a shaft portion 131 coupled to the rotor 122, a main bearing portion 132 rotatably radially supported by the first bearing portion 113, and a first scroll. An eccentric portion 133 eccentrically coupled to 140 and a sub bearing portion 134 rotatably supported in the second bearing portion 156 of the second scroll 150 in a radial direction are formed. As described above, the main bearing part 132 and the sub bearing part 134 respectively support the rotation shaft 130 in the radial direction, and the eccentric part 133 may rotate the rotational force of the driving motor 120 in the first scroll 140. The first scroll 140 is swiveled by the Oldham ring 180.

In addition, the axial bearing protrusion 135 described above may be formed to extend in the radial direction in the middle of the rotation shaft 130, that is, between the main bearing part 132 and the eccentric part 133. The axial bearing surface 135a of the axial bearing protrusion 135 forms a thrust surface together with the axial bearing surface 113a of the first bearing portion 113.

In addition, an oil supply passage 136 is formed inside the rotary shaft 130 by a predetermined depth in a direction from the rear end to the front end, and the main bearing part 132 and the eccentric part in the middle of the oil supply passage 136. 133, the respective oil supply holes 137a, 137b, 137c are formed toward the outer circumferential surface of the sub bearing portion 134. This will be described later along with the oil supply structure.

On the other hand, referring to Figure 2, the compression unit 105, as described above, is supported in the frame 112 of the main housing 110 in the axial direction to rotate the rotating scroll (hereinafter, first scroll) ( 140 and a fixed scroll (or non-orbiting scroll) (hereinafter referred to as a first scroll) that is engaged with the first scroll 140 and fixedly coupled to the second end 110b that forms the closed end of the main housing 110. 150). Two pairs of compression chambers V are formed between the first scroll 140 and the second scroll 150 during the pivoting movement of the first scroll 140. The compression chamber will be described later with the turning wrap and the fixing wrap.

The first scroll 140 is supported in the axial direction by the frame portion 112, and the anti-rotation mechanism for preventing the rotation of the first scroll 140 between the frame portion 112 and the first scroll 140. As the Oldham ring 180 is provided. The anti-rotation mechanism may be applied to pins and rings as well as olddam rings.

In addition, the first scroll 140 is a rotating scroll hard plate portion (hereinafter, the rotating hard plate portion) 141 is formed in a substantially disk shape, the front surface of the rotating hard plate portion 141 is engaged with the fixed wrap 153 to be described later Swivel wraps 142 forming compression chambers are formed on the inner and outer surfaces of the fixing wrap 153. The turning lap will be described later with the fixed lap.

The pivoting plate portion 141 is formed with a back pressure hole 141a for communicating the back pressure chamber S3 and the intermediate compression chamber V to each other. Accordingly, the oil or the refrigerant moves between the back pressure chamber S3 and the intermediate compression chamber V according to the difference between the pressure in the back pressure chamber S3 and the pressure in the intermediate compression chamber V.

In addition, a rotation shaft coupling portion 143 through which the eccentric portion 133 of the rotation shaft 130 is rotatably coupled is formed at the center of the pivot plate 141. The rotating shaft coupling portion 143 is formed in a cylindrical shape, and the third bearing 173 forming a bearing surface is inserted into and coupled to the eccentric portion 133 of the rotating shaft coupling portion 143. Accordingly, the rotating shaft coupling portion (or the third bearing) 143 is formed to overlap the turning wrap 142 in the radial direction, and the rotating shaft coupling portion 143 is a part of the turning wrap 142 formed at the innermost portion. do.

On the other hand, the second scroll is coupled to the second end of the main housing outside the main housing as described above. In this case, a sealing member such as a gasket may be provided between the main housing and the second scroll.

6 is a cross-sectional view showing a second scroll according to the present embodiment, and FIG. 7 is a front view showing the second scroll according to FIG. 6 from the front side.

As shown in the drawing, the second scroll 150 has a fixed scroll hard plate portion (hereinafter, fixed hard plate portion) 151 having a substantially disc shape, and the edge of the fixed hard plate portion 151 of the main housing 110. A side wall portion 152 is formed that is coupled to the frame side end. The front surface of the fixed plate portion 151 is formed with a fixed wrap 153 is engaged with the turning wrap 142 to form a compression chamber (V). The fixed wrap 153 may be formed in an involute shape together with the turning wrap 142, but may be formed in various other shapes. The shape of the fixed wrap 153 will be described later with reference to FIG. 8 along with the turning wrap 142.

In addition, the outer circumferential surface of the side wall portion 152 is formed to protrude in the radial direction so as to correspond to the first protrusion 114 described above, and the first flow passage 114a described above in the second protrusion 154. In addition, a second flow path 154a constituting the suction flow path Fg may be formed. Accordingly, the outer diameter center Oso of the second scroll 150 may be formed to have a center different from the center Ob2 of the second bearing portion 113.

The second flow path 154a constituting the suction flow path Fg may be formed in the axial direction, or may be inclined as shown in FIG. 6. When the second flow path 154a is formed in the axial direction, the outer diameter of the fixed hard plate part 151 may be enlarged to increase the wound length of the fixed wrap 153 relative to the same outer diameter of the main housing 110. When the 154a is formed to be inclined, the compressor may be miniaturized by reducing the wound length of the fixed wrap 153 to the same capacity of the compression chamber.

In addition, as the first flow passage 114a and the second flow passage 154a constituting the suction flow path Fg are formed in the first protrusion 114 and the second protrusion 154, respectively, the suction flow path Fg is formed in the compressor. It may be formed close to the outer peripheral surface. Accordingly, the refrigerant sucked into the compression chamber (V) through the suction flow path (Fg) in the motor chamber (S1) can be quickly heat exchanged with the outside of the compressor, through which the body of the refrigerant sucked into the compression chamber (V) Lowering the enemy can reduce suction loss. In particular, in the case of the second flow path 154a, since the second scroll 150 is provided outside the main housing 110, the second scroll 154a is located closer to the outside than that inserted into the main housing 110. The heat dissipation effect of the somewhat heated refrigerant can be further increased while passing through the seal.

In addition, the outer circumferential surface of the side wall portion 152 may be provided with a weight loss groove 152a for preventing deformation while reducing the weight of the second scroll 150. The weight gain groove 152a may be formed at a plurality of intervals along the circumferential direction, or one may be formed long in the circumferential direction.

Furthermore, since the outer circumferential surface of the side wall portion 152 of the second scroll 150 is located outside the main housing 110, the outer diameter of the second scroll 150 is greater than or equal to the inner diameter of the main housing 110. Can be formed. Thus, the outer diameter of the second scroll 150 can be increased based on the outer diameter of the same compressor, and through this, the length of the fixed wrap 153 and the turning wrap 142 is increased to increase the wound diameter of the compression chamber V. Inhalation volume can be increased.

In addition, a discharge port 155 is formed at the central portion of the fixed plate portion 151 to communicate the final compression chamber V with the oil separation chamber S3 to be described later to guide the discharge of the refrigerant. The discharge port 155 may be formed to penetrate in the axial direction or the inclined direction of the fixed plate portion 151 from the compression chamber (V) toward the oil separation chamber (S3). Only one discharge port 155 may be formed to communicate with both the first compression chamber V1 and the second compression chamber V2, which will be described later, as shown in FIG. 8, and the first compression chamber V1 and the second compression chamber may be formed. The first discharge port 155a and the second discharge port 155b may be formed to communicate with each other independently of the V2.

In addition, a second bearing portion 156 is formed at the center of the fixed plate portion 151 so that the sub bearing portion 134 of the rotation shaft 130 is rotatably inserted to be supported in the radial direction. The second bearing portion 156 may be formed to extend in the axial direction from the fixed plate portion 151 toward the rear housing 160, or may be formed by enlarging the thickness of the fixed plate portion 151 thickly. However, in the latter case, not only the weight of the second scroll 150 is increased, but also the unnecessary portion is formed to be thick, the length of the discharge port 155 may be increased, thereby increasing the dead volume. Accordingly, as shown in the former, a part of the fixed hard disk part 151 is protruded, for example, a third protrusion 157 is formed at a portion except for a portion where the discharge hole 155 is formed, and the third protrusion 157 is formed on the third protrusion 157. It is preferable to form the two bearing parts 156.

The second bearing portion 156 is formed in a cylindrical shape in which the rear surface is blocked, and the second bearing 172 forming the bearing surface with the sub bearing portion 134 of the rotating shaft 130 is inserted into and coupled to the inner circumferential surface thereof. The second bearing 172 may be made of a bush bearing or may be made of a needle bearing.

In addition, an oil guide space 156a extending in the axial direction from the end of the rotation shaft 130 is formed inside the rear side of the second bearing portion 156, and the oil guide space 156a is an oil guide flow path 157a which will be described later. ) And the oil supply passage 136. The oil guide flow path 157a is provided in the oil separation chamber S2, and the oil supply flow path 136 is formed in each bearing surface of the outer circumferential surfaces of the main bearing part 132, the sub bearing part 134, and the eccentric part 133. Can be communicated with.

The oil guide passage 157a may be formed in the second scroll 150 or may be formed in the rear housing 160 which will be described later. For example, when the oil guide flow path 157a is formed of the second scroll 150, the frame portion 112 is formed on the rear surface of the second scroll 150, that is, on both sides in the axial direction of the second scroll 150. When the surface facing the first surface 150a and the opposite surface of the first surface 150a are referred to as the second surface 150b, the second surface 150b protrudes in the direction toward the rear housing 160. The third protrusion 157 may be formed, and the oil guide passage 157a may be formed in the third protrusion 157 in the radial direction. One end of the oil guide passage 157a may be in communication with the outer circumferential surface of the fixed plate portion 151, and the other end of the oil guide passage 157a may be in communication with the inner circumferential surface of the oil guide space 156a.

Accordingly, the high pressure oil separated from the refrigerant in the oil separation chamber S2 of the rear housing 160 is quickly moved to the oil guide space 156a along the oil guide passage 157a by the pressure difference. Can be quickly supplied to each bearing surface through the oil supply passage 136 and the respective oil supply holes 137a to 137c by the pressure difference.

Referring back to FIG. 5, one oil guide passage 136 and a plurality of oil supply holes 137a, 137b, and 137c may be formed in the rotation shaft 130. As described above, the oil guide passage 136 is formed in the axial direction by a predetermined depth in the front end direction at the end of the rotation shaft 130, that is, the rear end of the rotation shaft 130 accommodated in the oil guide space 156a, The plurality of oil supply holes 137a, 137b, and 137c may be formed at regular intervals along the axial direction in the middle of the oil guide passage 136.

The plurality of oil supply holes 137a, 137b, and 137c pass through the second oil supply hole 137b penetrating the outer circumferential surface of the sub bearing part 134 and the third oil supply hole 137c penetrating the outer circumferential surface of the eccentric portion 133. The first oil supply hole 137a may pass through the outer circumferential surface of the main bearing part 132.

Accordingly, the oil flowing into the oil guide passage 136 from the oil guide space 156a passes through the second oil feed hole 137b, the third oil feed hole 137c, and the first oil feed hole 137a in turn. It is supplied to the bearing surface of.

Meanwhile, the turning wrap and the fixed wrap may each be formed in an involute shape. However, when the rotary shaft is coupled through the center of the second scroll, which is the orbiting scroll, as in this embodiment, the final compression chamber may be formed at an eccentric position, and a large pressure difference between the compression chambers may be generated. This is because, in the case of the axial through scroll compressor, the final compression chamber is eccentrically formed from the center of the scroll, so that the pressure in one compression chamber is significantly lower than the pressure in the other compression chamber. Therefore, in the axial through scroll compressor, it is advantageous to form the turning wrap and the fixed wrap in a non-involute shape as in the present embodiment.

8 is a plan view illustrating a coupling relationship between a non-involute shape swing wrap and a fixed wrap in the electric compressor according to the present embodiment.

As shown therein, the turning wrap 142 according to the present embodiment has a form in which a plurality of circular arcs having different diameters and origins are connected to each other, and the outermost curve may be formed in an approximately elliptical shape having a long axis and a short axis. have. The fixed wrap 153 may likewise be formed.

A central portion of the pivot plate 141 forms an inner end of the pivot wrap 142, and a rotation shaft coupling portion 143 through which the eccentric portion 133 of the rotation shaft 130 is rotatably inserted and coupled is formed in the axial direction. Can be. A third bearing 173 made of a bush bearing may be inserted into and fixed to an inner circumferential surface of the rotation shaft coupling part 143. The outer circumferential portion of the rotating shaft coupling portion 143 is connected to the turning wrap 142 to form a compression chamber V together with the fixed wrap 153 in the compression process.

In addition, the rotation shaft coupling portion 143 is formed at a height overlapping the pivot wrap 142 on the same plane, and the eccentric portion 133 of the rotation shaft 130 is disposed at the height overlapping the pivot wrap 142 on the same plane. Can be. As a result, the repulsive force and the compressive force of the refrigerant are offset to each other while being applied to the same plane based on the pivot plate, so that the inclination of the first scroll 140 due to the action of the compressive force and the repulsive force may be prevented.

In addition, the rotating shaft coupling portion 143 is formed with a recess 143a which engages with the protrusion 153a of the fixed wrap 153, which will be described later, on an outer circumferential portion facing the inner end of the fixed wrap 153. One side of the 143a is formed with an increasing portion 143b that increases in thickness from the inner circumference portion to the outer circumference portion of the rotary shaft coupling portion 143 along an upstream side of the compression chamber V in the forming direction. This makes the compression path of the first compression chamber V1 immediately before the discharge longer, so that the compression ratio of the first compression chamber V1 can be increased closer to the compression ratio of the second compression chamber V2.

The other side of the recess 143a is formed with an arc compression surface 143c having an arc shape. The diameter of the circular arc compression surface 143c is determined by the inner end thickness of the fixed wrap 153 (ie, the thickness of the discharge end) and the turning radius of the turning wrap 142. Increasing increases the diameter of the arc compression surface 143c. As a result, the thickness of the turning wrap around the circular arc compression surface 143c may be increased to ensure durability, and the compression path may be longer to increase the compression ratio of the second compression chamber V2.

In addition, a protruding portion 153a protruding toward the outer circumferential portion of the rotating shaft coupling portion 143 is formed near the inner end (suction end or starting end) of the fixed wrap 153 corresponding to the rotating shaft coupling portion 143. The contact portion 153b protruding from the protrusion portion and engaged with the recess portion 143a may be formed in the 153a. That is, the inner end of the fixed wrap 153 may be formed to have a larger thickness than other portions. As a result, the wrap strength of the inner end portion that receives the greatest compressive force among the fixed wraps 153 may be improved, thereby improving durability.

On the other hand, the compression chamber (V) is formed between the fixed hard plate portion 151 and the fixed wrap 153, and the turning wrap 142 and the rotating hard plate portion 141, the suction chamber, the intermediate pressure chamber along the direction of the wrap The oil separation chamber may be formed continuously.

The compression chamber V includes a first compression chamber V1 formed between the outer surface of the turning wrap 142 and the inner surface of the fixed wrap 153, and the inner surface and the fixed wrap 153 of the turning wrap 142. The second compression chamber (V2) is formed between the outer surface of the. That is, the first compression chamber V1 includes a compression chamber formed between two contact points P11 and P12 generated by contact between the inner surface of the fixed wrap 153 and the outer surface of the turning wrap 142. 2 The compression chamber V2 includes a compression chamber formed between two contact points P21 and P22 generated by contact between the outer surface of the fixed wrap 153 and the inner surface of the turning wrap 142.

Here, the first compression chamber V1 immediately before the discharge has an angle having a larger value among the angles formed by the center of the eccentric portion, that is, the center O of the rotary shaft coupling portion and the two lines connecting the two contact points P11 and P12, respectively. When? Is?, At least immediately before the discharge start,? <360 ° and the distance l between the normal vectors at the two contact points P11 and P12 also has a value greater than zero.

Since the fixed wrap and the swing wrap according to the present embodiment have a smaller volume than the case where the first compression chamber immediately before the discharge has the fixed wrap and the swing wrap formed of the involute curve, the swing wrap 142 And the compression ratio of the first compression chamber V1 and the compression ratio of the second compression chamber V2 may be improved without increasing the size of the fixing wrap 153.

Meanwhile, the rear housing 160 is coupled to the second surface 150b of the second scroll 150, and the compression chamber together with the second surface 150b of the second scroll 150 inside the rear housing 160. Oil separation chamber (S2) may be formed to accommodate the refrigerant discharged from (V).

Here, the fastening bolt passing through the edge of the rear housing 160 may be coupled to the edge of the second scroll 150. A sealing member such as a gasket may be provided between the rear housing 160 and the second scroll 150.

In addition, an exhaust port 161 through which the discharge tube communicates is formed in the rear housing 160, and protrudes toward the third protrusion 157 of the second scroll 150 inside the rear housing 160 to form a second scroll ( A support protrusion 162 supporting the axial direction 150 may be formed. The support protrusion 162 may be in close contact with the second surface 150b of the second scroll 150, more precisely, with the third protrusion 157, to support the second scroll 150 toward the first scroll 140. .

On the other hand, the inverter housing 210 may be coupled to the opposite end of the rear housing 160, that is, the open end of the main housing 110, from both ends of the main housing 110.

Referring again to FIGS. 1 and 2, the inverter housing 210 forms part of the inverter module 201, and the inverter housing 210 forms an inverter chamber S4 between the inverter cover 220 and the inverter cover 220. . In the inverter chamber S4, an inverter component 230 such as a substrate and an inverter element is accommodated, and the inverter housing 210 and the inverter cover 220 are bolted to each other. The inverter cover 220 may be assembled to the inverter housing 210 after the inverter housing 210 is first assembled to the main housing 110 first, or after the inverter housing 210 and the inverter cover 220 are assembled first. The inverter housing 210 may be assembled to the main housing 110. The former and the latter may be classified according to the manner in which the inverter housing 210 is assembled to the main housing 110.

For example, the fastening groove 210a may be formed on the edge of the inverter housing 210, and the fastening hole 220a may be formed on the edge of the inverter cover 220. The inverter housing 210 and the inverter cover 220 may be assembled by bolts that pass through the fastening holes 220a and are fastened to the fastening grooves 210a.

In this case, the inverter module 210 and the inverter cover 220 may be fastened to assemble the inverter module 201 first, and then the inverter module 201 may later be fastened to the main housing 110 forming the compressor module 101. have. Through this, not only the assembly of the inverter module is easy, but also the inverter device constituting the inverter module may be assembled to be in close contact with or close to the side of the inverter housing, thereby increasing the heat dissipation effect of the inverter device.

In addition, when the inverter housing 210 is coupled to the main housing 110 to seal the motor chamber S1 of the main housing 110 as in the present embodiment, the space between the main housing 110 and the inverter housing 210 may be increased. It must be tightly sealed to prevent leakage of refrigerant. To this end, sealing the motor chamber S1 by inserting a sealing member between the main housing 110 and the inverter housing 210 may increase the sealing force. This will be described again with the assembly structure of the main housing and the inverter housing.

In the electric compressor according to the present embodiment as described above, the refrigerant and the oil are circulated as follows.

That is, when power is applied to the driving motor 120, the rotation shaft 130 rotates together with the rotor 122 to transmit rotational force to the first scroll 140, and the first scroll 140 is Oldhamling. It is to be rotated by 180. Then, the compression chamber (V) is continuously moved toward the center side is reduced in volume.

Then, the refrigerant flows into the motor chamber S1 which is the suction space through the inlet 101a, and the refrigerant introduced into the motor chamber S1 is formed in the outer circumferential surface of the stator 121 and the inner circumferential surface of the main housing 110. Alternatively, the air is sucked into the compression chamber V through a suction flow path Fg provided in the main housing 110 and the second scroll 150 through the gap between the stator 121 and the rotor 122.

Then, the refrigerant is compressed by the first scroll 140 and the second scroll 150 to be discharged to the oil separation chamber S2 through the discharge port 155, and the refrigerant is separated from the oil separation chamber S2. The refrigerant is discharged into the refrigeration cycle through the exhaust port 161, while the oil is supplied through the oil guide passage 157a, the oil guide space 156a, the oil supply passage 136, and the oil supply holes 137a to 137c constituting the oil supply passage. It is supplied to each bearing surface, a part of the oil is introduced into the back pressure chamber (S3) to form a back pressure for supporting the first scroll 140 toward the second scroll 150.

Then, the first scroll 140 is supported in the direction toward the second scroll 150 by the back pressure of the back pressure chamber S3 to compress the chamber V between the first scroll 140 and the second scroll 150. ) Will be sealed. At this time, some of the oil in the back pressure chamber (S3) flows into the compression chamber (V) through the back pressure hole (141a) provided in the turning plate 141, while some oil is made of the main bearing portion 132 and 1 flows through the bearing 171 to the motor chamber (S1) and repeats a series of processes for the back pressure chamber (S3) to form a flow pressure as described above.

As such, the motor-driven compressor according to the present invention can simplify the manufacturing process of the compressor by easily forming the main frame by integrally forming the frame part in the main housing, thereby eliminating the processing process and the assembly process of the main frame. It is possible to reduce the processing error or assembly error caused. In addition, the concentricity of the transmission part and the compression part can be easily matched, the friction loss of the rotating shaft and the bearing wear can be reduced, and the outer diameter of the frame part can be increased compared to the same outer diameter of the main housing, so that the compressor can have a larger capacity than the same outer diameter. have. In addition, by extending a portion of the main housing provided with the frame portion to form a suction passage, it is possible to increase the design freedom of the suction passage.

In addition, the electric compressor according to the present invention can reduce the insertion depth of the drive motor by opening the side in which the inverter housing is coupled from both ends of the main housing to insert the drive motor. This can facilitate the assembly work of the drive motor, it is possible to maintain a constant concentricity with the main housing when assembling the drive motor. In addition, as the distance between the main housing and the inverter housing is reduced, the heat dissipation effect of the inverter element is increased, and the degree of assembly of the inverter element can be improved by modularizing the inverter housing and the inverter cover.

In addition, in the electric compressor according to the present invention, as the rotating shaft having the oil supply passage communicates with the oil separation chamber through the compression unit, the oil supply passage for guiding the oil separated from the oil separation chamber to the back pressure chamber can be simplified. In addition, the oil separated in the oil separation chamber can be quickly supplied to the bearing surface to reduce the friction loss. Furthermore, the motor chamber and the back pressure chamber may communicate with each other to allow the back pressure chamber to form a flow pressure, thereby allowing the oil to be smoothly supplied to the bearing surface.

On the other hand, as described above, the main housing and the member coupled to the main housing is usually fastened using a bolt, in this case, as the structure for fastening the bolt is additionally formed, the outer diameter of the compressor increases. For example, in the prior art, coupling parts 200a (not shown) are formed on the outer circumferential surfaces of the housing 200 and the rear head 300 or the housing 200 and the inverter casing 130, respectively, and fastened with bolts. As described above, the coupling portion protrudes from the outer circumferential surface of each member, thereby increasing the size of the compressor as a whole.

In this embodiment, the main housing and the inverter housing are fastened without forming fastening protrusions on the outer circumferential surfaces of both housings. 9 is an enlarged cross-sectional view of a coupling portion of the main housing and the inverter housing in FIG. 2.

As shown therein, the main housing 110 and the inverter housing 210 according to the present exemplary embodiment may include the first end 110a of the main housing 110 and the sealing surface 212 of the corresponding inverter housing 210. By fastening, the fastening member may be used rivets or bolts.

A plurality of rivet portions 116 protruding in the axial direction are formed at the first end 110a of the main housing 110, and riveting is provided at the sealing surface portion 212 of the inverter housing 210 facing the rivet portions 116. The rivet hole 215 through which the portion 116 is coupled may be formed.

The rivet part 116 may extend from the first end 110a of the main housing 110 by a predetermined length. The axial length of the rivet portion 116 may be formed to have a length that is equal to or substantially similar to the thickness of the inverter housing 210.

The rivet hole 215 may be formed through the axial direction between the outer surface and the inner surface of the sealing surface portion 212 of the inverter housing 210. The rivet hole 215 may be formed at predetermined intervals in the circumferential direction along the sealing surface portion 212 of the inverter housing 210.

In this embodiment configured as described above, by riveting the main housing 110 and the inverter housing 210, the first end 110a of the main housing 110 and the sealing surface 212 of the inverter housing 210 are mutually different. It can also be in close contact. However, it is preferable to insert a separate sealing member 190 such as a gasket between the main housing 110 and the inverter housing 210 to increase the sealing force between the main housing 110 and the inverter housing 210. .

When the sealing member 190 is a gasket, a difference in sealing force may occur depending on the shape of the gasket. For example, an annular gasket of simple plate may be used as in the prior art. However, in this case, the sealing member is positioned only between the first end 110a of the main housing 110 and the sealing surface portion 212 of the inverter housing 210, so that the sealing area can be narrowed and the sealing effect can be reduced. .

Thus, in the present embodiment, the sealing member 190 may be formed in an L shape to improve the sealing force between the main housing 110 and the inverter housing 210.

The sealing member 300 according to the present exemplary embodiment may include a first sealing part 191 in contact with the sealing surface part 212 and a second sealing part 192 in contact with an outer circumferential surface of the sealing protrusion 213 to be described later. . The first sealing part 191 and the second sealing part 192 may be separated from each other, or may be connected to each other and integrally formed. The embodiment looks at the center of an example in which the first sealing portion and the second sealing portion are integrally formed.

Since the rivet part 116 described above should be inserted into the rivet hole 215 in the first sealing part 191, a rivet passing hole 191a through which the rivet part 116 passes may be formed. The rivet passing hole 191a may be formed to have the same number and positions as the rivet part 116.

Meanwhile, a sealing protrusion 213 may be formed inside the sealing surface portion 212 of the inverter housing 210 to contact the inner circumferential surface of the second sealing portion. The sealing protrusion 213 may form a fourth protrusion and protrude in an axial direction to be inserted into the inner circumferential surface of the main housing 110.

As described above, the process of fastening the main housing and the inverter housing using the rivet is as follows.

First, the first sealing part 191 and the second sealing part 192 of the sealing member 190 are disposed in contact with the sealing surface 212 and the sealing protrusion 213 of the interlock housing 210. At this time, the rivet hole 191a provided in the first sealing portion 191 of the sealing member 190 corresponds to the rivet hole 215 provided in the sealing surface portion 212 of the inverter housing 210.

Next, the rivet part 116 extending from the first end 110a of the main housing 110 passes through the rivet through hole 191a of the sealing member 190 to the rivet hole 215 of the inverter housing 210. To be inserted. In this case, the inner circumferential surface of the main housing 110 is inserted into the outer circumferential surface of the sealing protrusion 213 of the inverter housing 210, and the second sealing portion 193 is positioned therebetween.

Next, the rivet portion 116 is pushed toward the rear side from the front surface of the inverter housing 210 so that the end portion of the rivet portion 116 is widely spread and close to the rivet hole 215. At this time, the end of the rivet portion 116 is in close contact with the inclined surface (215a) of the rivet hole 215 to be more closely fixed.

In this way, the first end of the main housing and the sealing surface of the inverter housing can be fastened without forming fastening protrusions on the outer circumferential surfaces of the main housing and the inverter housing, respectively. Accordingly, the outer diameter of the compressor is reduced compared to fastening both housings by forming fastening protrusions on the outer peripheral surfaces of the main housing and the inverter housing, thereby reducing the weight of the compressor and reducing the space required for installing the compressor. .

Furthermore, a sealing member made of a gasket is installed between the main housing and the inverter housing, and the sealing member is formed of the first sealing part and the second sealing part to seal the outer circumferential surfaces of the sealing surface part and the sealing protrusion, respectively. Accordingly, the sealing area is increased without increasing the thickness of the main housing and the inverter housing, so that the motor chamber can be more effectively sealed.

Furthermore, by forming the sealing protrusion in the inverter housing coupled with the main housing, it is possible to easily match the assembly position of the inverter housing when assembling the inverter housing to the main housing. Accordingly, the assembling work of the main housing and the inverter housing can be easily and accurately performed.

On the other hand, in the above-described embodiment, the end of the rivet portion is extended to be in close contact with the inclined surface of the rivet hole, or may be provided with an elastic member between the rivet portion and the rivet hole to allow the rivet portion to be elastically supported by the rivet hole.

10 is a cross-sectional view showing another embodiment of the rivet coupling structure in FIG. As shown therein, the front surface of the inverter housing 210 to be in close contact between the rivet portion 116 and the rivet hole 215, that is, the end portion 116a of the rivet portion 116 and the end portion 116a of the rivet portion. An elastic member 191a may be provided in an annular shape between the opposite surfaces of the sealing surface portion 212a.

Then, when the end portion 116a of the rivet portion 116 is pressed from the front side of the inverter housing 210, the end portion 116a of the rivet portion is stretched to be in close contact with the elastic member 191a.

Then, the elastic member 191a is pressed by the end portion 116a of the rivet portion to exert an elastic force, so that the rivet portion 116 is forced in the direction away from the front side, that is, the first end 110a of the main housing 110. do.

Then, as the first sealing part 191 is further compressed by the elastic member 191a, the space between the main housing 110 and the inverter housing 210 may be more closely sealed.

On the other hand, there is another embodiment of the main housing and the inverter housing according to the present invention as follows. 11 and 12 are cross-sectional views illustrating other embodiments of a coupling structure of the main housing and the inverter housing in FIG. 9.

For example, in the above-described embodiments, the rivet part 116 is integrally formed at the first end 110a of the main housing 110 and extends in the axial direction. The part 310 may be manufactured separately, and may be pressed into and coupled to the fastening groove 117 provided in the first end 110a of the main housing 110. In this case, the material of the rivet part 310 may be formed of a material different from that of the main housing 110.

That is, in the above-described embodiment, the rivet part and the main housing are formed of the same material as the rivet part is formed as a single body in the main housing. However, in the present embodiment, the material of the rivet part 310 may be formed in the material of the main housing 110. It does not restrict | limit, It can select suitably as needed. For example, the rivet part 310 in the present embodiment may be formed of a material having a higher rigidity than the main housing 110 in consideration of the bonding strength.

In the above embodiment, the fastening member is made of rivets, but is not necessarily limited to rivets. For example, a bolt may be used as the fastening member 320 as shown in FIG. 12. In this case, since the fastening member 320 is formed of a material that is harder than the material of the main housing 110, the fastening groove 117 is screwed to the fastening groove 117 so that the main housing 320 is damaged due to the riveting operation. It can prevent the fastening work.

Even when using the assembled rivet or bolt as the fastening member as described above, the shape of the sealing surface portion, the sealing protrusion and the sealing member may be formed in the same manner as in the above-described embodiment. In addition, since the basic structure and the effects thereof are the same, description thereof will be omitted.

In the above-described embodiments, the sealing member is formed of a gasket, but in some cases, a ring member such as an O-ring may be applied. 13 and 14 are cross-sectional views showing other embodiments of the sealing member in FIG. 9.

For example, as shown in FIG. 13, a sealing groove 213a may be formed on the outer circumferential surface of the sealing protrusion 213, and a sealing member 190, such as an O-ring, may be inserted into the sealing groove 213a. . Sealing member 190 is preferably formed of a high elastic material such as rubber can increase the sealing force is preferable.

Alternatively, as shown in FIG. 14, a first sealing member 196 made of a gasket is formed between the first end of the main housing and the sealing surface portion 212 of the inverter casing, and the inner circumferential surface of the main housing 110 and the outer circumferential surface of the sealing protrusion 213. O-ring second sealing member 197 may be provided between each. In this case, the first sealing member 196 is formed in an annular shape of a flat plate, a plurality of rivet passing holes 196a are formed to allow the rivet portion 116 to pass as shown in FIG. 9, and the second sealing member 197 may be inserted into and coupled to the sealing groove 213a provided in the sealing protrusion 213.

As described above, when the first sealing member 196 and the second sealing member 197 are formed of different members, the first sealing member 196 and the second sealing member 197 are assembled during assembly. Compared with the first sealing part and the second sealing part integrally formed, processing errors or cooking errors may be reduced, which may be advantageous to align the assembly positions. Furthermore, the material and the shape of the first sealing member and the second sealing member can be selected to further increase the sealing force.

101: compressor module 110: main housing
112: frame portion 113: first bearing portion
114: first protrusion 114a: first flow path
120: drive motor 121: stator
122: rotor 130: axis of rotation
132: main bearing portion 133: eccentric portion
134: sub bearing part 135: axial bearing protrusion
136: oil supply passage 137a to 137c: oil supply hole
140: first scroll (orbiting scroll) 142: orbiting wrap
150: second scroll (fixed scroll) 151: fixed plate part
153: fixed wrap 154: second protrusion
154a: second flow path 155: discharge port
156: second bearing portion 156a: oil guide space
157: third projection 157a: oil guide flow path
160: rear housing 162: support protrusion
171-173: Bearing 180: Olddam Ring
190: sealing member 191: first sealing part
191a: rivet passing hole 192: second sealing part
191a: elastic member 196: first sealing member
197: second sealing member 201: inverter module
210: inverter housing 212: sealing surface portion
212a: rivet ball 213: sealing protrusion
220: inverter cover 310: rivet portion
320: bolt S1: motor compartment
S2: oil separation chamber S3: back pressure chamber
S4: Inverter chamber V, V1, V2: Compression chamber
Fg: suction flow path

Claims (15)

Drive motor;
A first scroll eccentrically coupled to a rotational shaft coupled to the rotor of the drive motor to rotate;
A second scroll coupled to the first scroll to form a compression chamber;
A motor chamber coupled to the second scroll from the outside of the second scroll and the driving motor is coupled to form a suction space is formed, one side of the motor chamber is an open end, and the other side of the motor chamber is A main housing each having a frame portion for supporting the second scroll in an axial direction;
An inverter housing accommodating an inverter element electrically connected to the driving motor and coupled to an opening end of the main housing to seal the motor chamber; And
And an inverter cover coupled to the inverter housing on an opposite side of the main housing to form an inverter chamber.
Between the opening end of the main housing and the sealing surface portion of the inverter housing where the opening end of the main housing faces in the axial direction, a plurality of fastening portions for coupling the opening end of the main housing and the sealing surface portion of the inverter housing are circumferentially It is provided at predetermined intervals along the
Each of the plurality of fastening portions,
One end is fixed to the open end of the main housing, the other end is axially penetrating the inverter housing, characterized in that the electric compressor is fixed to the inner surface of the inverter housing. The method of claim 1,
The fastening part is a motor-driven compressor, characterized in that consisting of a plurality of rivets integrally extending in the axial direction at the open end of the main housing. The method of claim 1,
And the fastening part includes a plurality of rivets axially press-fitted to the opening end of the main housing. The method of claim 3,
The fastening unit is an electric compressor, characterized in that formed of a material different from the main housing. The method of claim 1,
The fastening unit is an electric compressor, characterized in that made of a bolt fastened to the open end of the main housing. The method of claim 5,
The fastening unit is an electric compressor, characterized in that formed of a material different from the main housing. The method of claim 1,
The one side of the sealing surface portion is formed in an annular and protruding in the axial direction sealing protrusions are formed, the sealing protrusion is characterized in that the motor is inserted into the opening end of the main housing. The method of claim 7, wherein
And a sealing member is provided between the main housing and the inverter housing. The method of claim 8, wherein the sealing member,
A first sealing part positioned between an opening end of the main housing and a sealing surface portion of the inverter housing facing the opening, and having a plurality of holes through the fastening part; And
And a second sealing part disposed between an inner circumferential surface of the main housing and an outer circumferential surface of a sealing protrusion of the inverter housing facing the inner circumferential surface of the main housing. The method of claim 9,
And the first sealing part and the second sealing part are integrally formed. The method of claim 9,
And the second sealing part is separated from the first sealing part and has a ring shape inserted into an inner circumferential surface of the main housing or an outer circumferential surface of a sealing protrusion of the inverter housing. The method of claim 8,
The sealing member is an electric compressor, characterized in that the ring shape located between the inner peripheral surface of the main housing and the outer peripheral surface of the sealing protrusion of the inverter housing. Drive motor;
A first scroll eccentrically coupled to a rotational shaft coupled to the rotor of the drive motor to rotate;
A second scroll coupled to the first scroll to form a compression chamber;
A motor housing in which the driving motor is coupled to form a suction space, and one side of the motor chamber is formed with an open end;
An inverter housing accommodating an inverter element electrically connected to the driving motor and coupled to an opening end of the main housing to seal the motor chamber; And
And an inverter cover coupled to the inverter housing at an opposite side of the main housing to form an inverter chamber.
On one side of the sealing surface portion of the inverter housing facing the open end of the main housing is formed a sealing protrusion protruding annularly and inserted into the open end of the main housing,
A sealing member is provided between the open end of the main housing and the sealing surface portion of the inverter housing, wherein the sealing member is
A first sealing part positioned between an opening end of the main housing and a sealing surface part of the inverter housing facing the opening end; And
And a second sealing portion that is bent from the first sealing portion and extends integrally and positioned between the inner circumferential surface of the main housing and the outer circumferential surface of the sealing protrusion of the inverter housing facing the same. The method of claim 13,
The first scroll is eccentrically coupled to the rotation axis through the axial direction,
The second scroll is a motor-driven compressor, characterized in that the rotating shaft penetrating the first scroll is rotatably inserted and supports the rotating shaft in the radial direction. The method according to claim 13 or 14,
The opening end of the main housing extends in the axial direction and a plurality of rivets are formed at predetermined intervals along the circumferential direction
A plurality of rivet through holes are formed in the first sealing part to penetrate the rivet part,
And a plurality of rivet holes are formed in the sealing surface portion of the inverter housing so that the plurality of rivet portions pass through and are coupled thereto.

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