KR20170139393A - Motor operated compressor - Google Patents

Abstract

An electric compressor according to the present invention includes a drive motor, a revolving scroll, and a fixed scroll in an inner space of a casing. A control unit is provided outside the casing. An intake port of the casing is provided on the side where the control unit is provided around the drive motor. An exhaust port of the casing is provided on the side where the fixed scroll is provided. A communication passage is formed between the casing and a stator so refrigerant sucked into the inner space through the intake port passes through the drive motor and flows into a compression chamber. On the outer surface of the casing, a groove may be formed to surround an element of the control unit. Accordingly, when high-pressure refrigerant such as CO_2 refrigerant is applied, it is possible to minimize the deformation of the surface of the casing with an element attached thereto to a curved surface even if internal pressure of the casing rises, thereby increasing the bonding force or a heat radiation effect of an element.

Description

[0001] MOTOR OPERATED COMPRESSOR [0002]

The present invention relates to a compressor, and more particularly to an electric compressor applied to a vehicle.

2. Description of the Related Art Generally, compressors for compressing refrigerant in automotive air conditioning systems have been developed in various forms. Recently, electric compressors driven by electric motors using motors have been actively developed according to the tendency of electric parts to be electricized.

Among electric compressors, scroll compressors suitable for high compression ratio operation are mainly applied. In the scroll type electric compressor, a motor unit constituted by a rotary motor is provided in a closed casing, a compression unit including a fixed scroll and an orbiting scroll is installed on one side of the motor unit, and the motor unit and the compression unit are connected by a rotary shaft, Is delivered to the compression section. The rotating force transmitted to the compression section causes the orbiting scroll to swing with respect to the fixed scroll to form a pair of two compression chambers composed of a suction chamber, an intermediate compression chamber and a discharge chamber. The refrigerant is sucked into both compression chambers, Method.

Although the motor of an electric compressor is operated at a constant speed, recently, an inverter type compressor capable of varying the operation speed of the motor to meet various needs of consumers has been widely introduced. In an inverter type electric compressor, an inverter is usually mounted on the outer circumferential surface of a casing, and is electrically connected to a motor inside the casing by using a terminal installed through the casing.

However, since the electric compressor is driven by electricity, heat is generated in the motor and the inverter constituting the compressor, and this heat greatly affects the performance of the motor and the inverter. Therefore, various methods for solving such a heating problem are suggested. Among the various methods, a method of cooling the motor and the inverter by using the refrigerant flowing into the casing of the electric compressor is mainly known.

In this method, the refrigerant flowing into the casing through the inlet port passes directly between the stator and the rotor of the motor or between the stator and the inner circumferential surface of the casing, while directly cooling the motor. At the same time, Is indirectly cooled.

However, the inverter generates very high heat depending on the device. Nevertheless, there is a problem that the cooling efficiency of the inverter is lowered as it is indirectly cooled by the refrigerant sucked into the casing.

In addition, the flow rate of the refrigerant can be increased to increase the cooling efficiency. However, the refrigerant flow area in the portion adjacent to the inverter is narrowed, so that the suction resistance against the refrigerant increases, and the suction loss of the compressor is generated.

On the other hand, in addition to regulations on CFCs and HCFCs in refrigerants themselves, the use of HFCs has recently become more regulated and interest in environmentally friendly natural refrigerants is increasing. Hydrocarbons, ammonia, water, air, and carbon dioxide are known as natural refrigerants. Of these, carbon dioxide (CO ₂ ) is known to be useful in terms of miniaturization, high efficiency, high pressure, and low cost.

However, since the electric compressor using the CO ₂ refrigerant forms an internal pressure which is about eight times higher than that using the conventional R134a refrigerant, the casing can be elastically deformed as the casing swells up during operation. As a result, the surface of the casing is deformed like a curved surface, and the contact area with the switching element I101cBT attached to the casing is reduced. As a result, the adhesive force of the switching element is reduced and the compressor may be detached by the vibration of the compressor.

Also, if the casing is elastically deformed, the contact area between the switching element and the casing is reduced, and the heat dissipation effect for the switching element may be lowered. In view of this, conventionally, a heat transfer member such as a thermal pad is added between the casing and the switching element, which complicates the assembling process, thereby increasing the manufacturing cost. In addition, It is also difficult to use a separate fastening member such as a screw.

On the other hand, when the CO ₂ refrigerant is used, the internal pressure of the casing rises and the terminal connecting the motor and the external power source can be firmly fixed to maintain the reliability. In order to improve the weldability between the terminal and the casing, a part of the casing or the casing to which the terminal is welded is made of an iron (Fe) type metal such as a terminal, The total weight is increased. This increased the weight of the vehicle when installing the compressor in a vehicle, particularly an electric vehicle.

In addition, when the terminal is welded to the casing, if the casing is deformed or damaged, it is necessary to replace the terminal together, so that the material cost and the maintenance cost are increased.

On the other hand, in the conventional electric compressor, the stator is press-fitted and fixed to the inner peripheral surface of the casing. However, since the stator is laminated with a plurality of thin steel plates and a plurality of slots for winding the coils are formed on the inner circumferential surface, friction between the stator and the rotor is generated between the slots when the stator is press-fitted into the casing, Could be lowered.

In addition, as the stator is pressed into the casing, concentrated stress is applied to both ends of the stator in the axial direction. As a result, the stator is deformed and friction or noise is generated between the stator and the rotor.

On the other hand, in the conventional electric compressor, the back pressure space is formed on the back surface of the orbiting scroll. However, when CO ₂ refrigerant is used, the pressure in the back pressure space also increases and a high sealing force for the back pressure space is required. However, as the sealing force increases, the friction loss with the rotating shaft may increase, which may deteriorate the performance of the compressor. Therefore, there is a demand for a method capable of reducing the frictional loss with the rotary shaft while increasing the sealing force.

An object of the present invention is to provide an electric compressor in which a refrigerant sucked into a casing can effectively cool an inverter and a motor.

It is another object of the present invention to provide an electric compressor in which a refrigerant sucked into a casing is sucked into an inverter and flows into a compressor after passing through a motor.

Another object of the present invention is to provide an electric compressor suitable for applying an environmentally friendly refrigerant such as CO ₂ refrigerant.

Another object of the present invention is to provide an electric compressor in which an element constituting an inverter can stably maintain an adhered state even if a casing is swollen and deformed when a high-pressure refrigerant is applied.

It is another object of the present invention to provide an electric compressor capable of facilitating assembly of a terminal.

Another object of the present invention is to provide an electric compressor capable of forming a casing with a material different from that of the terminal.

Another object of the present invention is to provide an electric compressor capable of reducing the weight of a compressor by making a part of the casing made of a material lighter than iron.

Another object of the present invention is to provide an electric compressor capable of attenuating the concentrated stress applied to the stator when the stator is press-fitted into the casing.

Another object of the present invention is to provide an electric compressor capable of preventing the slot of the stator from being opened due to the press-fitting of the stator.

Another object of the present invention is to provide an electric compressor capable of simplifying a sealing portion forming a back pressure space.

It is another object of the present invention to provide an electric compressor capable of reducing frictional loss in a sealing part forming a back pressure space while applying CO ₂ refrigerant.

It is another object of the present invention to provide an electric compressor in which a back pressure space can be formed quickly.

In order to achieve the object of the present invention, there is provided a stator comprising: a stator wound with a coil; a driving motor having a rotor rotatably provided inside the stator; A rotating shaft coupled to the rotor to transmit rotational force of the driving motor; A orbiting scroll coupled to the rotating shaft and performing a turning motion; A fixed scroll engaged with the orbiting scroll and forming a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber together with the orbiting scroll; A frame provided on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween to support the orbiting scroll; A control unit provided on the opposite side of the frame with the drive motor interposed therebetween; And the control unit is provided on the outside, and the intake port is provided on the side where the control unit is provided with the drive motor as the center, the exhaust port on the side where the fixed scroll is provided, And a casing in which a communication passage is formed between the stator and the stator so that the refrigerant sucked into the inner space through the suction port flows into the suction chamber through the driving motor. May be provided. As a result, the control unit can be cooled using the cold refrigerant sucked through the intake port, thereby improving the cooling efficiency of the control unit.

The casing includes a housing to which a stator of the driving motor is coupled. A cover for sealing an inner space of the casing is coupled to one end of the housing at a side where the inlet port is formed, And a groove having a predetermined depth and width may be formed on the outer surface of the cover to which the device is coupled. The grooves may be formed along the perimeter of each element. Accordingly, when a high-pressure refrigerant such as CO ₂ refrigerant is applied, the surface of the casing with the device can be prevented from being deformed into a curved surface even if the internal pressure of the casing is increased, .

The cover may be made of a material that is lighter than the material of the housing. This reduces the weight of the compressor and can be particularly effective when applied to an electric vehicle.

A radiating fin or a heat dissipating groove is formed on the inner side surface of the cover so that the refrigerant sucked through the inlet port is heat-exchanged, or a chamber portion having a predetermined volume is formed on the inner surface of the cover. While the outlet can communicate with the inner space of the casing. As a result, the heat radiation effect of the device can be further enhanced.

The cover may be provided with a terminal mounting hole for connecting a terminal, and at least one end of the terminal inserted into the terminal mounting hole may be screwed to the fixing member. Thus, the fixing operation of the terminal is easy and the cover can be made of a light material, so that the weight of the compressor can be reduced.

The flange portion is formed at one end of the terminal with a flange portion larger than the inner diameter of the terminal mounting hole and the opposite end of the end portion at which the flange portion is formed is formed with a male screw portion, The male screw portion may pass through the terminal mounting hole and be fastened to the female screw portion of the fixing member on the outside of the casing.

A sealing member may be provided between the flange and one side of the casing corresponding to the flange or between the fixing member and the other side of the casing corresponding thereto. Thus, even when the internal pressure of the casing increases during application of the CO ₂ refrigerant, the refrigerant can be prevented from leaking to the joint portion of the terminal.

A plurality of teeth having a predetermined height are formed on an outer circumferential surface of the stator so as to be in contact with an inner circumferential surface of the casing in a circumferential direction And the protrusion may be formed so as to be located at least partially within the radial range of the teeth. Thereby, it is possible to prevent the slot from spreading due to the concentrated stress that the stator receives from the casing.

Further, the protrusion may be formed to be located within the arc length range of the tooth.

The arc length of the protrusion may be smaller than or equal to the arc length of the tooth.

The inner circumferential surface of the casing may be provided with a stress attenuating portion spaced apart from the outer circumferential surface of the stator, and the stress attenuating portion may be formed in at least one axial range of the stator.

The stress attenuator may be formed at a position where the axial end of the stator is received.

The frame is provided with a shaft hole through which the rotation shaft is inserted and whose inner circumferential surface faces the outer circumferential surface of the rotary shaft. One side of the shaft hole is opened toward the back surface of the orbiting scroll, A space may be formed between the inner circumferential surface of the shaft hole and the outer circumferential surface of the rotating shaft by oil introduced into the back pressure space. Accordingly, even when the pressure of the back pressure space increases when a high-pressure refrigerant such as CO ₂ refrigerant is applied, it is possible to reduce occurrence of friction loss due to excessive contact of the sealing portion with the rotary shaft.

At least one back pressure hole is formed in the fixed scroll and the frame so that the refrigerant discharged from the compression chamber and the oil communicate with the back pressure space. The total cross sectional area of the back pressure hole is determined by the inner circumferential surface of the shaft hole, Sectional area of the gap formed between the outer circumferential surfaces of the first and second protrusions. Thereby, the back pressure space can always be filled with an appropriate amount of oil.

The back pressure space may have a balance weight coupled to the rotation shaft. The height of the back pressure hole may be equal to or lower than the middle height of the balance weight when the axial direction of the driving motor is perpendicular to the axial direction. have.

A labyrinth seal may be formed on at least one of the inner circumferential surface of the shaft hole or the outer circumferential surface of the rotating shaft corresponding thereto. Thereby, the sealing force of the back pressure space can be improved.

An oil pocket may be formed on at least one of the inner circumferential surface of the shaft hole or the outer circumferential surface of the rotating shaft corresponding thereto.

The frame may have an oil supply hole communicating with the oil pocket. And the oil supply hole can communicate with the back pressure hole. Thereby, a sealing portion between the shaft hole and the rotary shaft can be formed quickly.

In order to achieve the object of the present invention, there is provided a stator comprising: a stator having a coil wound thereon; a motor part having a rotor rotatably provided inside the stator; A rotating shaft for transmitting a rotating force of the motor unit; A compression unit coupled to the rotary shaft for receiving the rotational force of the motor unit and compressing the refrigerant; A frame provided between the motor unit and the compression unit to support the rotation shaft; A control unit provided on the opposite side of the frame with the driving motor interposed therebetween; And an exhaust port on the side where the control unit is provided and an exhaust port on the side where the compression unit is provided, the exhaust port being provided on the side where the control unit is provided, A communication passage is formed between the stator and the stator so that the refrigerant sucked through the stator is passed through the driving motor and sucked into the stator, and an element is attached to the outer surface of the stator, And a casing in which a groove is formed along the circumference of the element.

Here, a radiating fin or a heat dissipating groove may be formed on the inner surface of the casing to which the device is attached.

Further, in order to achieve the object of the present invention, A compression unit provided inside the casing for sucking, compressing, and discharging the refrigerant; A rotating shaft for transmitting power to the compression unit; A rotor coupled to the rotating shaft and transmitting power to the rotating shaft; And a plurality of annular stator cores are stacked in the axial direction and press-fitted into the inner circumferential surface of the casing, and a plurality of teeth wound on the inner circumferential surface of the casing are arranged along the circumferential direction with a slot therebetween And a plurality of protrusions formed on the outer circumferential surface along the circumferential direction to contact the inner circumferential surface of the casing, wherein the protrusions are formed so that at least a part of the protrusions are located within the arc length range of the teeth. A compressor may be provided.

Here, the inner circumferential surface of the casing may be provided with a stress attenuating portion spaced apart from the outer circumferential surface of the stator, and the stress attenuating portion may be formed within at least one axial range of the stator.

Further, in order to achieve the object of the present invention, A stator fixed to the casing; A rotor rotatably disposed inside the stator; A rotating shaft coupled to the rotor and rotating together; A orbiting scroll coupled to the rotating shaft and performing a turning motion; A fixed scroll engaged with the orbiting scroll and forming a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber together with the orbiting scroll; A shaft hole is formed on the opposite side of the orbiting scroll to support the orbiting scroll and the shaft hole is inserted through the shaft hole so that the inner circumferential surface of the shaft hole faces the outer circumferential surface of the rotating shaft, And a back pressure space is formed at a side of the orbiting scroll with a back surface of the orbiting scroll, and a space between the inner circumferential surface of the shaft hole and the outer circumferential surface of the rotating shaft is sealed by oil introduced into the back pressure space. And an electric compressor (not shown).

The frame has an oil supply hole communicating with the inner side surface of the back pressure space. The sectional area of the back pressure hole is larger than or equal to the total sectional area of the interval formed between the inner peripheral surface of the shaft hole and the outer peripheral surface of the corresponding rotary shaft .

The motor-driven compressor according to the present invention is provided with an intake port on a side where a control unit is provided with a drive motor as its center, an exhaust port on a side where a fixed scroll constituting a compression section is provided, The control unit can be cooled by the refrigerant sucked through the inlet port, and the cooling efficiency of the control unit can be increased.

Further, since the element constituting the control unit is attached to the outer surface of the casing and a groove having a predetermined width is formed along the periphery around the element, when the high-pressure refrigerant such as CO ₂ refrigerant is applied, It is possible to minimize the deformation of the surface of the casing in which the device is attached to the curved surface, thereby increasing the bonding force and heat radiation effect of the device.

In addition, the casing is provided with a terminal mounting hole for connecting the terminal, and the terminal inserted into the terminal mounting hole is welded or screwed with a fixing member, so that the fixing operation of the terminal is easy, So that the compressor can be made lightweight.

A plurality of projections having a predetermined height are formed on the outer circumferential surface of the stator along the circumferential direction so as to be brought into contact with the inner circumferential surface of the casing. The projections are formed at least partially within the radial range of the teeth, The friction between the rotor and the impact noise can be prevented.

The frame has a shaft hole through which the rotating shaft passes and a back pressure space communicating with the shaft yoke to support the back surface of the orbiting scroll. The back pressure space is sealed by inducing oil at a sealing interval between the shaft hole and the rotating shaft, It is possible to simplify the structure for sealing the back pressure space and to reduce the occurrence of friction loss due to excessive contact of the sealing portion with the rotary shaft even when the pressure of the back pressure space is increased when high pressure refrigerant such as CO ₂ refrigerant is applied .

1 is a longitudinal sectional view showing the inside of a scroll compressor which is an example of an electric compressor according to the present invention,
Fig. 2 is a perspective view showing the appearance of the casing in the scroll compressor according to Fig. 1,
FIGS. 3 and 4 are longitudinal sectional views showing embodiments of the terminal coupled state in FIG. 2. FIG.
Fig. 5 is a perspective view of the front cover separated from the device in Fig. 2,
FIG. 6A is a vertical cross-sectional view for explaining and comparing the prior art for the "VI-VI" line in FIG. 5,
Fig. 6B is a longitudinal sectional view for explaining the embodiment of the "VI-VI" line in Fig. 5,
7A and 7B are longitudinal sectional views showing the heat radiation fins and the heat dissipating grooves provided on the inner surface of the front cover in FIG. 2,
FIG. 8 and FIG. 9 are a vertical sectional view and a plan view showing a heat radiation chamber provided on the inner surface of the front cover in FIG. 2,
FIG. 10 is a vertical sectional view showing a compression portion for explaining an embodiment of a sealing portion of a back pressure space in the scroll compressor according to FIG. 1;
Fig. 11 is a vertical sectional view showing a compression section for explaining another embodiment of the sealing section of the back pressure space in the scroll compressor according to Fig. 1; Fig.
Fig. 12 is a longitudinal sectional view showing an enlarged view of the back sealing bore and the second sealing portion between the rotating shaft and the frame in Fig. 11,
Figs. 13 and 14 are longitudinal sectional views showing other embodiments of the second sealing portion in Fig. 12,
FIG. 15 is a perspective view showing a stator in the scroll compressor according to FIG. 1,
16 is a front view showing a state where the stator according to Fig. 15 is pressed into the housing, Fig.
Fig. 17 is a longitudinal sectional view showing an enlarged part of a stator in Fig. 16,
18 is a longitudinal sectional view showing a state in which a stator is press-fitted into a housing in the scroll compressor according to Fig.

Hereinafter, an electric compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.

FIG. 1 is a longitudinal sectional view showing the inside of a scroll compressor which is an example of an electric compressor according to the present invention, and FIG. 2 is a perspective view showing an appearance of a casing in the scroll compressor according to FIG.

As shown in the figure, the scroll compressor according to the present embodiment is characterized in that a frame 102 is fixed to the center of a casing 101, a driving motor 103 for generating a driving force is installed on one side of the frame 102, A compression section 104 for receiving the driving force of the driving motor 103 and compressing the refrigerant may be installed on the other side of the frame 102. A control unit (hereinafter abbreviated as an inverter) 106 for controlling the operation of the compressor may be provided outside the casing 101. The inverter 106 may be located on the opposite side of the compression section when the drive motor 103 is referred to.

The orbiting scroll 150 includes a fixed scroll 140 and an orbiting scroll 150. The orbiting scroll 150 is eccentrically coupled to a rotary shaft 135 coupled to the rotor 132 of the drive motor 103, A pair of compression chambers P consisting of a suction chamber, an intermediate pressure chamber, and a discharge chamber are formed together with the fixed scroll 140 while performing a swing motion with respect to the scroll 140. [

As shown in FIGS. 1 and 2, the casing 101 is formed in a cylindrical shape having open ends at both ends thereof, and includes a housing 111 constituting a suction space V1, a housing 111 coupled to cover the rear side of the housing 111, A rear cover 112 which forms a discharge space V2 along with the rear surface of the housing 140 and an inverter space V3 which is coupled to cover the front side of the housing 111 and which is coupled with an inverter cover 161 to be described later And a front cover 113 for supporting the front cover 113.

The suction space V1 is divided into a first space V11 and a second space V12 by the drive motor 103. The first space V11 and the second space V12 are connected to the driving motor 103 Through a plurality of communication passages 101c formed between the outer circumferential surface of the stator 131 of the housing 111 and the inner circumferential surface of the housing 111. [ The first space V11 is formed together with the front cover 113 and the second space V12 is formed together with the frame 102. [ The refrigerant is sucked into the first space V11 on the side of the front cover 113 and then moved to the second space V12 on the side of the frame 102 through the driving motor 103. [

1 and 2, the housing 111 is formed with a stator support surface (hereinafter referred to as a first support surface) 111a in which the stator 121 of the drive motor 120 is axially supported in the middle of the inner periphery thereof And a frame supporting surface (hereinafter, referred to as a second supporting surface) 111b in which the back surface of the frame 102 is axially supported can be formed on the inner circumferential surface rear side. The first support surface 111a may be formed in an annular stepped shape, or may be formed in a circular arc shape having a predetermined interval along the circumferential direction.

The housing 111 may be provided with an inlet 101a through which a suction pipe is connected to guide the refrigerant into the suction space V1 of the housing 111. [ The intake port 101a may be formed to be positioned between the front end of the drive motor 103, which is the opposite side of the compression section, and the front cover 113, with respect to the drive motor 103. [ Thereby, the refrigerant flows into the internal space of the casing 101 through the intake port 101a, and can be sucked into the compression section after passing the drive motor 103 from the front side to the rear side. In addition, the coolant may first come into contact with the front cover 113 to cool the switching element 166 attached to the front cover 113 before cooling the driving motor 103.

As shown in FIG. 1, the rear cover 112 is formed in a circular plate shape, and a fastening protrusion 112a protruding forward from the outer periphery of the rear cover 112 and closely contacting the rear surface of the housing 111 may be formed in an annular shape. The inner circumferential surface of the fastening protrusion 112a may be formed with a sealing protrusion 112b which is inserted into the inner circumferential surface of the housing 111 and closely in radial direction.

Between the rear cover 112 and the housing 111, a leakage preventing sealing member 111e such as an o-ring may be provided to prevent refrigerant discharged from being leaked.

An exhaust port 101b is formed at the center of the front surface of the rear cover 112 and connected to the discharge pipe so as to guide the refrigerant compressed by the compression unit to the refrigeration cycle. An oil is separated from the refrigerant discharged into the exhaust port 101b An oil separator 185 may be formed.

Meanwhile, the front cover 113 may be formed in a disk shape and may be hermetically sealed to the front surface of the housing 111. A sealing member 111f such as an o-ring may be provided at a portion where the rear surface (inner surface) of the front cover 113 and the front surface of the housing 111 are in contact with each other.

A terminal mounting hole 113a is formed in the front cover 113 and an external power source is connected to the coil of the driving motor 103 by connecting the terminal 182 to the terminal mounting hole 113a. The inner side surface of the terminal mounting hole 113a may be formed so as to be stepped so that the flange portion 182a of the terminal 182 is engaged with the stepped surface so as to be tightly coupled.

Here, the terminal 182 may be welded to the front cover 113, or may be detachably fastened using a separate fixing member 183.

Figs. 3 and 4 are longitudinal sectional views showing embodiments of the terminal coupled state in Fig. 2. Fig.

3, a flange portion 182a having an outer diameter larger than the inner diameter of the terminal mounting hole 113a is formed at the inner end of the terminal 182 so as to extend over the inner surface of the front cover 113, The periphery of the outer edge of the terminal 182 can be welded (W) from the outside of the front cover 113 through the terminal mounting hole 113a.

Here, since the terminal 182 is formed of an iron-based metal, the front cover 113 may also be formed of an iron-based metal. A sealing member such as an o-ring may be provided between the flange portion 182a of the terminal 182 and the inner surface of the front cover 113 corresponding thereto.

4, the inner end of the terminal 182 is provided with an outer diameter larger than the inner diameter of the terminal mounting hole 113a so as to extend over the inner surface of the front cover 113 A flange portion 182a is formed and a male screw portion 182b fastened to a female screw portion 183a provided on the inner circumferential surface of the fixing member 183 may be formed at the outer end of the terminal 182. [

This allows the male threaded portion 182b of the terminal 182 to be inserted into the terminal mounting hole 182a in a state in which the flange portion 182a of the terminal 182 is caught by the inner surface of the front cover 113 in the periphery of the terminal mounting hole 113a. And can be fastened to the female threaded portion 183a of the fixing member 183 from the outside of the front cover 113 through the opening 113a.

Here, a sealing member 184 such as an o-ring may be provided between the flange portion 182a of the terminal 182 and the inner surface of the front cover 113 corresponding thereto. The terminal 182 and the front cover 113 are sealed by the input of the fixing member in the case of using the fixing member unlike the method in which the terminal is fixed by welding so that the terminal 182 and the front cover 113 It may be necessary to interpose the sealing member 184 between the sealing member 184 and the sealing member 184.

Accordingly, even though the terminal 182 is formed of a ferrous metal, the front cover 113 does not need to be made of a heavy metal such as iron, and the weight of the overall compressor can be reduced by forming the front cover 113 from a relatively light aluminum material.

On the other hand, the control unit 106 may be installed on the front side of the front cover 113. [ The control unit 106 has the inverter cover 161 having the inverter accommodating space V3 coupled to the front surface of the front cover 113 and the rotational speed of the drive motor 103 in the inverter accommodating space V3 And an inverter 162 for controlling the inverter 162 may be combined.

Fig. 5 is a perspective view of a front cover separated from the device in Fig. 2, Fig. 6a is a longitudinal sectional view for explaining a prior art for the "VI-VI" line in Fig. 5, FIG. 7A and FIG. 7B are longitudinal sectional views showing the heat radiation fins and heat dissipating grooves provided on the inner surface of the front cover in FIG. 2, and FIGS. 8A and 8B are longitudinal cross- And FIG. 9 is a vertical sectional view and a plan view showing a heat radiation chamber provided on the inner surface of the front cover in FIG.

1 and 5, the inverter 162 includes a plurality of switching elements (Insulated 101cate Bipolar Transistor: I101 cBT) 165 attached to the front surface of the front cover 113, And an inverter board 166 provided thereon.

Since the switching element 165 generates high heat when the compressor is driven, a heat transfer member such as a thermal sheet is attached to the front surface of the front cover 113 to dissipate the heat, and the front surface of the heat transfer member , The outer surface) of the switching element 166 can be attached.

However, when the thermal sheet is used, the number of parts increases, which not only increases the material cost but also increases the number of assembly operations.

In addition, in a compressor using a high-pressure refrigerant such as CO ₂ refrigerant, the inner pressure of the casing 101 is greatly increased as compared with the case of using a general refrigerant such as 134a refrigerant, so that the front cover 113 can expand and contract 6A, the contact area between the front cover 113 and the switching element 166 decreases and the switching element 166 contacts the front cover 113. As a result, And the heat radiation effect may be reduced.

5, a deformation restricting groove 113b may be formed on the front surface of the front cover 113, that is, around the switching element 166 to have a predetermined depth and width. The deformation restricting groove 113b may be formed so as to surround the circumference of the switching element 166. [ Accordingly, even if the front cover 113 is inflated by the internal pressure as shown in Fig. 6B, deformation of the front cover 113 due to the deformation restricting groove 113b can be minimized. Therefore, the contact area between the switching element 166 and the front cover 113 can be secured widely, and the switching element 166 can be effectively radiated without using a separate thermal sheet.

5, the switching element 166 may be fastened to the front cover 113 using a screw 168. In this case, In this case, since no separate bonding member such as a thermal sheet is provided between the switching element 166 and the front cover 113, screwing can be facilitated. As a result, the switching element 166 can be more firmly and stably fixed to the front cover 113. In the drawing, reference numerals 113c denote screw grooves.

7A and 7B, the front cover 113 may be formed with the heat radiating fin 113d or the heat radiating groove 113e on the inner surface of the front cover 113. [ As a result, the heat transfer area of the front cover 113 and the refrigerant can be enlarged to further enhance the heat dissipation effect of the switching element 166.

Here, when the radiating fin 113d or the radiating groove 113e is formed, the radiating fin 113d or the radiating groove 113e is formed in a direction intersecting the axial direction of the inlet 101a so that the contact area with the coolant can be enlarged But it may be formed in a direction coinciding with the axial direction of the inlet port 101a to increase the flow rate of the refrigerant.

The radiating fins 113d or the radiating grooves 113e may be formed in a straight line, but may be formed in a curved shape or a maze-like shape so that the refrigerant can circulate the front cover 113 evenly.

8 and 9, the heat radiation chamber 164 may be provided on the inner surface of the front cover 113 to forcibly guide the refrigerant toward the inner surface of the front cover.

In this case, the inlet 164a of the heat dissipation chamber 164 is formed toward the inlet port 101a while the outlet 164b is formed toward the internal space of the casing 101. [ Although the inlet 164a and the outlet 164b may be formed on the same straight line, it may be preferable that the refrigerant is formed as different as possible so that the refrigerant can circulate evenly in the inner space of the heat-

The inlet 164a may be spaced apart from the inlet 101a of the casing 101 by a predetermined distance but may be connected to the inlet 164a of the heat-dissipating chamber 164 to allow the refrigerant to be sucked through the heat- May be directly connected to the inner end of the intake port.

However, depending on the surrounding conditions such as the coil of the stator 131, the inlet 164a of the heat dissipation chamber 164 may be extended to be adjacent to the intake port 101a as much as possible and the direction of the intake port 101a may be formed in the heat dissipation chamber 164 in the direction of the entrance.

The radiating fins 113d or the heat dissipating grooves 113e described above may be formed on the front surface of the front cover 113 in the inside of the heat dissipation chamber 164.

The refrigerant flowing into the internal space of the casing 101 through the inlet 101a flows into the interior of the heat dissipation chamber 164 through the inlet of the heat dissipation chamber 164 and flows through the outlet 164b into the casing (The first space) V11 of the inner space 101 (the first space).

As a result, the cold refrigerant flowing into the inner space of the casing 101 comes into contact with the front cover 113 to cool the front cover 113, so that the switching element 166 attached to the front cover 113 can be effectively Can be cooled.

On the other hand, a space may be formed in the frame together with the fixed scroll and the orbiting scroll, and a back pressure space for supporting the orbiting scroll in the fixed scroll direction by the pressure of the space portion may be formed.

FIG. 10 is a longitudinal sectional view showing a compression part to explain an embodiment of a sealing part of a back pressure space in the scroll compressor according to FIG. 1, and FIG. 11 is a longitudinal sectional view showing a sealing part of a back pressure space, 12 is an enlarged vertical cross-sectional view of the second sealing portion between the back pressure hole and the rotary shaft and the frame in Fig. 11, and Fig. 13 and Fig. 14 are longitudinal sectional views showing the compression portion 2 is a longitudinal sectional view showing another embodiment of the sealing portion.

As shown in FIG. 1, the frame 102 may be inserted into and fixedly coupled to the opening end of the housing 111. The frame 102 may be supported on the second supporting surface 111b provided on the inner circumferential surface of the front end of the housing 111 to be axially supported.

The frame 102 is formed in a disk shape and has a frame side rigid plate portion 121 (hereinafter referred to as a first rigid plate portion) 121. The frame 102 protrudes from the front face of the first rigid plate portion 121, Side sidewall portions (hereinafter referred to as first sidewall portions) 122 to which the sidewall portions 142 are coupled. A thrust surface 123 is formed inside the first sidewall part 122 and supported by the orbiting scroll 150 in the axial direction. A refrigerant discharged from the compression chamber P A back pressure space 124 for supporting the back surface of the orbiting scroll 150 can be formed. A shaft hole 125 through which the rotation shaft 135 passes is formed in the back pressure space 124 and a main bearing 171 which will be described later can be installed on the shaft hole 125.

The back pressure space 124 is a space formed by the frame 102, the fixed scroll 140 and the orbiting scroll 150. The back pressure space 124 is a space formed by the frame 102, the fixed scroll 140 and the orbiting scroll 150, A first sealing portion 191 provided in the frame 123 and a second sealing portion 192 provided between the shaft hole 125 of the frame 102 and the outer peripheral surface of the rotary shaft 135.

The first sealing part 191 is formed by annularly forming a first sealing groove 123a having a predetermined depth on the thrust surface 123 of the frame 102 and the first sealing groove 123a is formed with a ring- One sealing member 195 can be inserted. The first sealing member 195 can be seated between the orbiting scroll 150 and the first sealing member 195 while being pushed up by the force of the pressure of the back pressure space 124.

10, a second sealing groove 125a is formed in the inner circumferential surface of the shaft hole 125 of the frame 102, and a second sealing groove 125a is formed in the second sealing groove 125a. 2 sealing member 196 may be inserted.

However, when a high-pressure refrigerant such as CO ₂ refrigerant is applied, the pressure in the back pressure space 124 also greatly increases. However, if the pressure in the back pressure space 124 is high, the contact area between the second sealing member 196 and the rotating shaft 125 increases, and the friction loss between the second sealing member 196 and the rotating shaft 125 increases .

In view of this, as shown in FIGS. 11 and 12, the second sealing portion can be formed by using the viscosity of the oil without applying the solid sealing member. As a result, the frictional loss with the rotary shaft can be effectively reduced while maintaining the pressure in the high backpressure space.

That is, the second sealing portion 192 forms a minute sealing interval t1 between the inner peripheral surface of the shaft hole 125 and the outer peripheral surface of the rotary shaft 135, and the inner peripheral surface of the shaft hole 125 and the inner peripheral surface of the rotary shaft 135 The oil flows into the space between the outer circumferential surfaces to form the oil film 192a and the pressure of the back pressure space 124 can be maintained by the oil film 192a.

Here, the oil filled in the second sealing portion 192 may be utilized as the oil introduced into the back pressure space 124 together with the refrigerant discharged from the compression chamber (P). To this end, a back pressure hole may be formed in the fixed scroll 140 and the frame 102 to guide a part of the refrigerant discharged from the compression chamber P into the back pressure space 124 together with the oil.

A first back pressure hole 147 is formed in the fixed scroll 140 through the second sidewall portion 142 at its rear surface and a first back pressure hole 147 of the fixed scroll 140 is formed in the frame 102. [ A second back pressure hole 127 communicating with the back pressure space 124 may be formed to pass from the rear surface of the first side wall portion 121 to the inner wall surface of the back pressure space 124.

The height of the outlet end 127a of the second back pressure hole 127 is set to a height enough to allow the oil in the back pressure space 124 to be filled with the oil seal at the second sealing portion 192 at all times, The height of the balance weight 175 that rotates in the space 124 is set to a height at which the balance weight 175 is locked so that the load on the motor can be prevented from being increased or the noise can be prevented from being increased due to the stirring of the balance weight 175 .

At this time, in order for the amount of oil filled in the back pressure space 124 to be always maintained at a constant amount, the amount of oil discharged from the back pressure space 124 must be greater or at least the same. For this purpose, it is preferable that the entire cross-sectional area of the second sealing portion 192 (more precisely, the cross-sectional area excluding the oil film formed due to the viscosity) is formed to be smaller than or at least equal to the entire cross-sectional area of the second back pressure hole 127.

On the other hand, the second sealing portion 192 may be formed with an oil pocket so that a predetermined amount of oil can be filled. For example, as shown in FIG. 13, the oil pocket 125b having a predetermined volume may be formed on the inner peripheral surface of the shaft hole 125, or the oil pocket may be formed on the outer peripheral surface of the rotation shaft corresponding to the inner peripheral surface of the shaft hole .

In this case, an oil supply hole 128 for directly supplying oil to the oil pocket 125b may be formed. The oil supply hole 128 may be formed through the fixed scroll 140 and the frame 102 separately from the back pressure hole 127 described above but may be branched from the middle of the back pressure hole. Accordingly, when the compressor is started, the oil quickly moves to the oil pocket 125b to form the second sealing portion 192, so that the appropriate pressure in the back pressure space 124 can be formed quickly.

As shown in Fig. 14, a labyrinth seal 125c may be further formed on the inner peripheral surface of the shaft hole 125. As shown in Fig. This prevents the oil in the back pressure space 124 from leaking through the second sealing portion 192 or prevents the pressure in the back pressure space 124 from leaking before the back pressure space 124 is filled with oil can do.

On the other hand, the stator of the driving motor can be press-fitted into the housing.

Fig. 15 is a perspective view showing a stator in the scroll compressor according to Fig. 1, Fig. 16 is a front view showing a state in which a stator according to Fig. 15 is pushed into a housing, Fig. And FIG. 18 is a longitudinal sectional view showing a state in which a stator is press-fitted into a housing in the scroll compressor of FIG.

1, the driving motor 103 includes a stator 131 fixed to the inside of the housing 111 and a rotor 131 positioned inside the stator 131 and rotated by the interaction between the stator 131 and the stator 131 132 < / RTI > The stator 131 is fixed to the inside of the housing 111 and fixed to the stator 131. The rear end of the stator 131 is supported on the first supporting surface 111a provided on the inner circumferential surface of the housing 111 .

15, the stator 131 is formed by stacking a plurality of thin steel plates and has a plurality of teeth 131a and slots 131b so as to wind the coil C on the inner circumferential surface thereof. They can be alternately formed continuously.

When the stator is press-fitted into the inner circumferential surface of the housing 111, the stator is spaced apart by a predetermined distance between the stator 131 and the inner circumferential surface of the housing 111 to form a communication passage 101c through which refrigerant or oil can move A plurality of support protrusions 131c may be formed. The support protrusions 131c are formed between both ends along the axial direction of the stator 131 and the support protrusions 131c may be spaced apart from each other by a predetermined distance along the circumferential direction.

As shown in Figs. 16 and 17, the support protrusion 131c may be formed so as to be radially in-line with the teeth 131a or within a radial range of the teeth.

For example, when the stator 131 is press-fitted into the housing 111, the support protrusion 131c of the stator 131 is pressed against the inner circumferential surface of the housing 111, The pressing force F is transmitted to the teeth 131a or the slots 131b formed on the inner peripheral surface of the stator 131. [

When the position of the support protrusion 131c, that is, the arc length range? 1 of the support protrusion is located within the circumferential length? 2 of the slot 131b, the support protrusion 131c is pushed by the housing 111, (F) is transmitted to the slot 131b, so that the teeth 131a located on both sides of the slot 131b are opened. When the gap between the teeth 131a is opened, the entire stator may be deformed, and friction may be generated between the stator and the rotor 132.

Therefore, it may be important to prevent the pushing force F, which is generated when the support protrusion 131c is pressed against the housing 111, to be transmitted to the slot 131b of the stator as much as possible. To this end, the support protrusions 131c are formed so as to be located in the same line CL1 and CL3 in the radial direction with the teeth 131a so that the pressing force F applied to the support protrusions 131c is transmitted to the slots 131b So that it can be canceled through the teeth 131a.

In this embodiment, the arc length range? 1 of the support protrusion 131c can be formed within the arc length range? 3 of the tooth 131a. Here, the circular arc length range 3 of the tooth 131a extends laterally outward from the center on both circumferential side surfaces 131a ', 131a " of each tooth 131a, and two imaginary lines L1 And the arcuate length? 3 generated by connecting the imaginary lines L1 and L2 with the circular line L3. Both ends of the support protrusions 131c extend in the circular arc length range of the teeth 131a 3 or at least within the range.

At least one of the ends 131c 'and 131c' of the support protrusion 131c may be positioned within the range 3 and the other end may be located outside the range 3. However, The center line CL3 passing through the center of the arc length of the support protrusion 131c is positioned within the arc length range of the tooth 131a As shown in FIG.

It is preferable that the arc length of the support protrusion 131c is formed to be smaller than or equal to the arc length (width length) of the teeth 131a. If the arc length of the support protrusion 131c is larger than the width of the tooth 131a, a pressing force transmitted to the support protrusion 131c may be transmitted to the slot 131b so that the slot 131b may be opened. Therefore, it is preferable that the arc length of the support protrusion 131c is formed to be smaller than the arc length of the tooth 131a, and it is preferable that the arc length of the support protrusion 131c is not larger than the arc length of the teeth 131a.

Thus, even if the support protrusion 131c is brought into close contact with the housing 111 and receives a force F pressed from the housing 111, the force is not transmitted to the slot 131b but mostly transmitted to the teeth 131a to be canceled It is possible to prevent the gap between the teeth 131a of the stator from being deformed in advance.

Further, when the stator is press-fitted into the housing, both ends of the stator can receive a concentrated load from the housing. 18, stress relieving portions may be formed on the inner circumferential surface of the housing 111 to prevent stress from concentrating on both ends of the stator 131 when the stator 131 is press-fitted. The stress attenuation portion may be formed of an inclined surface 111c or an undercut 111d formed on the inner peripheral surface of the housing 111. [

The inclined surface 111c may be formed in a shape in which the stator 131 is press-fitted, that is, the inner diameter of the housing 111 is increased from the front side to the front side. Accordingly, when the stator 131 is press-fitted, the stator 131 is pressed along the inclined surface 111c, so that the stator 131 can be easily press-fitted. Since the outer circumferential surface of the front end 131d of the stator 131 is spaced apart from the inner circumferential surface of the housing 111 by a predetermined gap g1 after the stator 131 is press-fitted, It is possible to prevent the stress from concentrating on the front end 131d of the stator 131 by the force.

The undercut 111d has a predetermined depth and width within the range including the rear end 131e of the stator 131 at the position where the rear end 131e of the stator 131 is pressed, that is, on the rear side of the housing 111 . Accordingly, even when the stator 131 is press-fitted, the rear end 131e of the stator 131 and the inner circumferential surface of the corresponding housing 111 are spaced apart from each other by a predetermined gap g2, Stress can be prevented from being concentrated on the stator 131 by the housing 111. The undercut 111d may be formed continuously on the front side of the first support surface 111a.

1, the rotary shaft 135 includes a shaft portion 135a coupled to the rotor 132 and an eccentric portion 135b coupled to the boss portion 153 of the orbiting scroll 150 . The eccentric portion 135b may be inserted into an eccentric bearing 173 to be described later to transmit the rotational force to the orbiting scroll 150. [

An oil passage 135c for supplying oil to the sliding portion is formed inside the rotary shaft 135 and an oil which is poured into the discharge space V2 of the casing 101 is provided at the rear end of the oil passage 135c, And an oil pump 136 for pumping the oil into the oil chamber 135c. The oil pump 136 is formed by a trochoid gear pump so that the inner ring 136a is coupled to the rotary shaft 135 while the outer ring 136b is inserted into the pump insertion portion 113f provided on the rear side of the front cover 113 Can be combined.

The shaft portion 135a may be supported radially by the main bearing 171 and the sub bearing 172 on both sides of the rotor 122 in the front and rear directions.

The main bearing 171 is composed of a ball bearing in which the outer ring is inserted into the frame 102 and the inner ring is inserted into the rotary shaft 135. The sub bearing 172 has its outer ring connected to the pump inserting portion 113f, And a ball bearing inserted and coupled to the rotating shaft 135, respectively.

On the other hand, the fixed scroll (140) has a fixed side end plate portion (hereinafter referred to as a second end plate portion) 151 formed in a disk shape, and a fixed side wall portion (Hereinafter referred to as a second sidewall portion) 142 is formed at a central portion of the second hard plate portion 141. A fixed lap (not shown) is formed at the center of the second hard plate portion 141 to form a pair of two compression chambers P 143 are formed.

A suction port (not shown) communicating with the suction space V1 of the casing 101 is formed at the edge of the second hard plate portion 141 and a discharge port A discharge port 144 communicating with the discharge port V2 may be formed. A first back pressure hole 147 may be formed at one side of the discharge port 144 so that a part of the refrigerant and oil discharged through the discharge port 144 is guided to the back pressure space 124.

The orbiting scroll 150 is formed in a disk shape with a swiveling side plate portion (hereinafter referred to as a third plate portion) 151 and is protruded toward the second plate portion 141 on the front face of the third plate portion 151 And a boss portion 152 formed on the rear surface of the third hard plate portion 151 and coupled to the rotary shaft 135 with an eccentric bearing 173 interposed therebetween to receive a rotational force, (153) may be formed.

In the drawing, reference numeral 170 is an anti-rotation member.

The assembling process of the scroll compressor according to the present embodiment as described above is as follows.

That is, the stator 131 of the drive motor 103 is shrunk and joined to the housing 111. At this time, the rear end of the stator 131 is seated on the first support surface 111a provided on the inner circumferential surface of the housing 111, so that the stator 131 can be prevented from flowing backward.

The supporting protrusion 131c provided on the outer circumferential surface of the stator 131 is pressed against the inner circumferential surface of the housing 111 and the support protrusion 131c is pressed against the pressing protrusion 131c. However, since the supporting protrusion 131c is formed on the same line as the teeth 131a of the stator 131, the pressing force F is transmitted in the direction of the teeth 131a without being transmitted in the direction of the slot 131b, The slot 131b can be prevented from being opened while being canceled by the slot 131a.

It is also possible to receive concentrated stress at both ends 131d and 131e of the stator 131 while the stator 131 is press-fitted. However, both ends of the stator 131 may be inclined to the inner peripheral surface of the corresponding housing 111 The gaps g1 and g2 are formed between the inner circumferential surface of the housing 111 and the outer circumferential surfaces of both ends 131d and 131e of the stator 131 corresponding to the inner circumferential surface of the stator 131, Can be eliminated in the radial direction. Therefore, it is possible to prevent the stator 131 from being deformed after press-fitting.

Next, the rotor 132 to which the rotating shaft 135 is coupled is inserted into the stator 131. At this time, the sub-bearing 172 is inserted and fixed to the rotating shaft 135.

Next, the frame 102 is seated and coupled to the housing 111. At this time, the housing 111 is provided with the second supporting surface 111b, and the rear surface of the frame 102 is seated on the second supporting surface 111b so that the frame 102 can be prevented from flowing in the axial direction .

Next, the anti-rotation member 170, the orbiting scroll 150, and the fixed scroll 140 are placed on the frame 102, and then the fixed scroll 140 is bolted to the frame 102. Then, the front cover 113 is mounted on the front surface of the housing 111 and bolts to fasten the inverter cover 161 to complete the assembly of the scroll compressor.

However, it is also possible to fasten the front cover 113 to the housing 111 after the inverter cover 114 is fastened to the front cover 113 first. At this time, various components 166 for controlling the inverter and the inverter package 167 to which the elements 166 are coupled are bolted to the outer surface of the front cover 113, and terminals 182 Are assembled by using the welding W or the fastening member 83.

Thus, even if the internal pressure of the casing 101 rises in a compressor using the high-pressure refrigerant such as CO ₂ refrigerant, the terminal 182 can be completely sealed to the front cover 113 and thus the assembly of the terminal 182 It is possible to prevent the site from being damaged. Particularly, when the terminal 182 is assembled using the fastening member 183, the front cover 113 can be made of a material that is lighter than other casings, thereby reducing the weight of the compressor. At the same time, even if the front cover 113 is damaged and replaced, the terminal 182 can be recycled, so that the maintenance cost can be reduced.

The operation and effect of the scroll compressor according to the present embodiment as described above are as follows.

That is, when power is applied to the drive motor 103, the rotation shaft 135 rotates together with the rotor 132 of the drive motor 103 to transmit the rotational force to the orbiting scroll 150.

The orbiting scroll 150 is rotated by an eccentric distance by the eccentric portion 135b of the rotary shaft 135 and the rotation preventing member 170 so that the compression chamber P is continuously moved toward the center side, .

The refrigerant introduced into the first space V11 flows into the first space V11 through the inlet 101a and the outer peripheral surface of the stator 131 of the driving motor 103 and the outer surface of the housing 111 Through the gap between the stator and the rotor and toward the compression portion, and is then sucked into the compression chamber (P). At this time, as the front cover 113 forms the first space V11 together with the housing 111, the refrigerant sucked into the first space V11 through the intake port 101a passes through the driving motor 103 The inner surface of the front cover 113 comes into contact first before flowing into the second space V12. Accordingly, the front cover 113 is cooled by heat exchange with the cold suction refrigerant, and thus the heat generated in the switching element 166 attached to the outer surface of the front cover 113 can be quickly dissipated. Thereafter, the refrigerant passes through the stator 131 to cool the driving motor.

The refrigerant sucked into the compression chamber P is compressed while being moved toward the center side along the movement path of the compression chamber P and is discharged through the discharge port 144 to the discharge port 140 formed between the fixed scroll 140 and the rear cover 102 And is discharged in the space V2.

Then, the refrigerant discharged to the discharge space V2 separates oil from the discharge space V2 or moves to the oil separator 185 to separate the oil from the refrigerant, and the refrigerant flows through the exhaust port 101b into the refrigeration cycle While the separated oil is recovered to the inner space of the housing 111 through the oil passage (not shown). The recovered oil is pumped by the oil pump 136 and circulated to the sliding section.

Here, a part of the refrigerant and oil discharged into the discharge space V2 flows into the back pressure space 124 through the first back pressure hole 147 of the fixed scroll 140 and the second back pressure passage 127 of the frame 102 And the refrigerant and the oil form back pressure in the back pressure space 124 to support the orbiting scroll 150 in the fixed scroll direction.

The back pressure space 124 includes a first sealing portion 191 formed between the frame 102 and the orbiting scroll 105 and a second sealing portion 192 formed between the frame 102 and the rotation shaft 135, As shown in Fig. Particularly, since the second sealing portion 192 narrows the sealing interval t1 between the shaft hole 125 of the frame 102 and the rotary shaft 135, the oil in the back pressure space 124 is sealed at the sealing interval t1 To form an oil film and oil seal the sealing interval t1. Accordingly, even when CO ₂ refrigerant is used, the efficiency of the compressor can be improved by effectively reducing the back pressure space 124 and reducing the friction loss with the rotary shaft 135 at the second sealing portion 192.

When the oil pocket 125b is formed in the second sealing portion 192 or the labyrinth seal 125c is formed, the sealing effect can be further enhanced.

Claims (17)

A drive motor having a stator having a coil wound thereon and a rotor rotatably provided inside the stator;
A rotating shaft coupled to the rotor to transmit rotational force of the driving motor;
A orbiting scroll coupled to the rotating shaft and performing a turning motion;
A fixed scroll engaged with the orbiting scroll and forming a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber together with the orbiting scroll;
A frame provided on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween to support the orbiting scroll;
And a casing having the driving motor, the orbiting scroll, the casing accommodating the fixed scroll in an inner space and having an intake port, and a plurality of covers covering both sides of the housing,
Wherein a plurality of elements are coupled to an outer surface of one of the plurality of covers, and a groove having a predetermined depth and width is formed around the element on a surface to which the element is attached. The method according to claim 1,
Wherein the grooves are formed along the perimeter of each element. The method according to claim 1,
Wherein the cover is made of a material that is lighter than the material of the housing. The method according to claim 1,
And an inner side surface of the cover is formed with a heat dissipating fin or a heat dissipating groove so that refrigerant sucked through the suction port is heat-exchanged. 5. The method of claim 4,
Wherein the heat dissipation fin or the heat dissipation recess is formed in a direction crossing the axial direction of the intake port. 5. The method of claim 4,
Wherein the heat dissipation fin or the heat dissipation recess is formed in the same direction with respect to the axial direction of the intake port. The method according to claim 1,
A chamber portion having a predetermined volume is formed on an inner surface of the cover,
Wherein the inlet of the chamber portion communicates with the inlet port while the outlet communicates with the interior space of the casing. 8. The method of claim 7,
Wherein an inlet and an outlet of the chamber portion are formed on different lines. The method according to claim 1,
And said element is screwed to said cover. The method according to claim 1,
Wherein the cover is formed with a terminal mounting hole for engaging a terminal, and at least one end of the terminal inserted into the terminal mounting hole is screwed to the casing by a fixing member. 11. The method of claim 10,
Wherein one end of the terminal is formed with a flange portion larger than an inner diameter of the terminal mounting hole, and an opposite end of the end portion where the flange portion is formed is formed with a male screw portion,
And the male screw portion is fastened to the female screw portion of the fixing member at the other side of the cover portion through the terminal mounting hole in a state in which the flange portion is caught on one side of the cover at the periphery of the terminal mounting hole. . 12. The method of claim 11,
And a sealing member is provided between one side of the flange and the corresponding cover or between the fixing member and the other side of the cover corresponding to the flange. The method according to any one of claims 1 to 12,
The casing is provided with a suction port on a side to which the device is attached with the drive motor as a center, a discharge port on the side where the fixed scroll is provided,
And a communication passage is formed between the stator and the stator so that the refrigerant sucked into the internal space of the casing through the suction port flows into the suction chamber through the driving motor. A motor section having a stator wound with a coil and a rotor rotatably provided inside the stator;
A rotating shaft for transmitting a rotating force of the motor unit;
A compression unit coupled to the rotary shaft for receiving the rotational force of the motor unit and compressing the refrigerant;
A frame provided between the motor unit and the compression unit to support the rotation shaft;
A control unit provided on the opposite side of the frame with the driving motor interposed therebetween; And
Wherein the control unit is provided on an outer side and the air intake port is provided on the side where the control unit is provided and the air outlet is provided on the side where the compression unit is provided, And a casing in which a communication passage is formed between the stator and the stator so that the refrigerant sucked through the intake port passes through the driving motor and is sucked into the compression section,
Wherein the control unit includes at least one element attached to an outer surface of the casing, and an outer surface of the casing is formed with a deformation preventing groove along a circumference of the element. 15. The method of claim 14,
Wherein the surface to which the device is attached is flat at the room temperature. A drive motor having a stator having a coil wound thereon and a rotor rotatably provided inside the stator;
A rotating shaft coupled to the rotor to transmit rotational force of the driving motor;
A orbiting scroll coupled to the rotating shaft and performing a turning motion;
A fixed scroll engaged with the orbiting scroll and forming a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber together with the orbiting scroll;
A frame provided on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween to support the orbiting scroll;
A control unit provided on the opposite side of the frame with the drive motor interposed therebetween; And
Wherein the control unit is provided outside, the intake port is provided on the side where the control unit is provided with the drive motor as the center, the exhaust port on the side where the fixed scroll is provided, And a casing in which a communication passage is formed between the stator and the stator so that the refrigerant sucked into the inner space through the suction port flows into the suction chamber through the driving motor,
And an inner surface of the casing is formed with a heat dissipating fin or a heat dissipating groove so that the refrigerant sucked through the intake port is heat-exchanged. 17. The method of claim 16,
Wherein the casing includes a housing to which a stator of the driving motor is coupled, a cover for sealing an inner space of the casing is coupled to one end of the housing at which the inlet port is formed,
Wherein a plurality of elements are coupled to an outer surface of the cover and the radiating fins or heat dissipating grooves are formed on an inner surface of a cover to which the elements are coupled.

Images