KR101983051B1 - Motor operated compressor - Google Patents

Abstract

According to the present invention, an electric compressor can comprise: a casing having a sealed inner space; a first scroll fixed in the radial direction of the inner space of the casing; a second scroll rotating by being engaged with the first scroll to form a pair of compression chambers between the first scroll and the second scroll; a frame radially fixed at a side opposite to the first scroll, wherein the second scroll is formed between the first scroll and the frame; a drive motor disposed on a side opposite to the second scroll, wherein the frame is formed between the second scroll and the drive motor; and a rotary shaft wherein a first end portion passes through the frame, the second scroll, and the first scroll to form a fixing end supported in a radial direction, and a second end portion opposite to the first end portion based on the frame is coupled to a rotor of the drive motor to form a free end.

Description

[0001] MOTOR OPERATED COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly, to an electric compressor which is mainly applied to a vehicle including an electric 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. [0003] In the scroll type electric compressor, a closed scroll casing is provided with a transmission section formed as a rotary motor, a compression section including a fixed scroll and an orbiting scroll is installed on one side of the transmission section, Is transmitted 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.

In addition, an inverter type compressor capable of varying the operation speed of a motor, including a constant speed motor, is also being developed as an electric compressor. In the inverter-type electric compressor, the inverter is mounted on the outer circumferential surface or one side surface of the casing, and the inverter is electrically connected to a motor provided inside the casing using a terminal passing through the casing.

On the other hand, the scroll type compressor applied to the air conditioning system for a vehicle is mainly installed in the horizontal type in the engine room structure of the vehicle. Accordingly, the main frame and the subframe are respectively provided for supporting the rotation shaft on both lateral sides of the transmission portion as the transmission portion and the compression portion are arranged in the transverse direction and connected by the rotation shaft.

However, in the conventional electric compressor as described above, there is a problem in that the axial length of the compressor becomes long as the motorized portion is located on one side of the compression portion and the main frame and the subframe are positioned on both sides of the axial direction of the transmission portion.

In the conventional electric compressor, the inverter is provided on the side where the subframe is provided in the case of the low-pressure type, but the low-temperature refrigerant sucked into the internal space of the casing due to the subframe does not sufficiently contact the surface to which the inverter is coupled . As a result, the refrigerant can not effectively cool the inverter, and the compressor efficiency may be lowered due to overheating of the inverter.

In the conventional electric compressor, the oil is separated from the refrigerant discharged from the compression chamber into the discharge space, and the oil is supplied to the compression chamber or the bearing surface through the oil supply passage provided in the scroll or frame, It is difficult to form the oil passage and the oil supply passage is lengthened so that the oil can not be supplied quickly when the compressor is started.

In the conventional electric compressor, the rotation shaft is supported using ball bearings. However, this is because the cost and operation noise due to the ball bearing increase, the distance between the compression portion and the bearing is increased, and the tilting of the orbiting scroll increases, There is a problem that the refrigerant leakage of the refrigerant is increased.

The conventional electric compressor is configured to support the back surface of the orbiting scroll by the back pressure due to the compression chamber being formed only on one side of the orbiting scroll. However, this is because of the difference between the back pressure of the back pressure space and the axial gas force in the compression chamber There is a problem in that the behavior of the orbiting scroll becomes unstable due to the occurrence of the differential pressure, which limits the high-speed operation and lowers the compression efficiency due to the refrigerant leakage.

U.S. Patent Publication No. US 2014/0134032 A1 (Apr.

An object of the present invention is to provide an electric compressor capable of reducing the axial length of a compressor by supporting a rotary shaft at one axial side of the transmission portion.

It is another object of the present invention to provide an electric compressor in which suction refrigerant can effectively cool an inverter by narrowing an interval between an inlet and an inverter for guiding a suction refrigerant to an internal space of a casing.

It is another object of the present invention to provide an electric compressor that can easily form an oil supply passage for guiding oil to the suction portion and can supply oil quickly.

It is another object of the present invention to provide an electric compressor capable of reducing the cost due to the bearing supporting the rotary shaft, reducing operating noise, and reducing the gap between the compression unit and the bearing, thereby reducing refrigerant leakage in the compression chamber.

It is another object of the present invention to provide an electric compressor in which the compression chamber is formed on both sides of the orbiting scroll and the behavior of the orbiting scroll can be stabilized without providing a separate backpressure space.

In order to accomplish the object of the present invention, a casing is provided with a plurality of scrolls supported by a frame, a rotary shaft for transmitting the rotational force of the driving motor is coupled to any one of the scrolls, Is formed to be recessed in the axial direction toward the drive motor.

Here, one end of the rotary shaft may be spaced a predetermined distance in the axial direction from a plurality of bearing portions supported in the radial direction on the opposite side of the drive motor with respect to the frame.

Further, in order to achieve the object of the present invention, there is provided an air conditioner comprising: a casing having a sealed inner space; A first scroll fixed radially in an inner space of the casing; A second scroll that forms a pair of two compression chambers between the first scroll and the first scroll, while being pivotally engaged with the first scroll; A frame fixed in a radial direction opposite to the first scroll with the second scroll interposed therebetween; A driving motor provided on the opposite side of the second scroll with the frame therebetween; And a first end constituting a fixed end supported in a radial direction through the frame, the second scroll and the first scroll, and a second end opposite to the first end with respect to the frame, And a rotating shaft coupled to the free end of the housing to form a free end.

Here, the driving motor is formed such that a stator surrounding the rotor is coupled to the casing, a winding coil is wound on the stator, and a second end of the rotating shaft is formed so as to be positioned within an axial range of the winding coil .

One side of the casing protrudes toward the driving motor to form an inverter accommodating portion, and at least a part of the inverter housing accommodating the inverter element can be inserted into the inverter accommodating portion.

And, at least a part of the inverter accommodating portion may be formed so as to be located within the range of the winding coil.

An inner space of the casing is formed such that an inlet port is formed in a space where the drive motor is provided with respect to the frame and a suction pipe communicates with the space, and at least a part of the inverter accommodating portion is formed in a range of overlapping with the inlet port in a radial direction .

Here, the first end of the rotary shaft is formed with an eccentric portion that is eccentrically coupled to the second scroll, a first bearing portion and a second bearing portion are formed on both sides of the eccentric portion in the axial direction, The two bearing portions may be formed to have the same axial center line, and the eccentric portion may be formed to have a different axial center line from the first bearing portion or the second bearing portion.

The first scroll may include a bearing receiving protrusion protruding toward the casing to receive the second bearing portion of the rotating shaft.

The casing may have a bearing receiving protrusion protruding toward the first scroll to receive the second bearing portion of the rotating shaft.

At least one of the first bearing portion and the second bearing portion may be supported by a bush bearing.

Here, the rotary shaft is formed with oil supply grooves in the axial direction at the end of the first end to a predetermined length, and a plurality of oil supply holes are spaced apart in the axial direction so as to face the respective bearing portions and the eccentric portions in the oil supply grooves .

The oil supply groove may be provided with a pressure reducing member for reducing the pressure of the oil.

The second scroll is formed with a swinging lap at one side contacting with the first scroll, a rotation axis coupling part through which the rotation axis passes and eccentrically coupled to the center of the swinging lap is formed between the second scroll and the frame, And a pressure of the back pressure space may be an intermediate pressure between an internal space pressure of the casing and a final pressure of the compression chamber.

The first scroll and the second scroll are engaged with the first and second orifices so as to form a compression chamber, respectively, in the first scroll and the frame, respectively, A first stationary wrap and a second stationary wrap may be formed.

The internal space of the casing is divided into a first space where the driving motor is provided and a second space opposite to the first space with respect to the frame, and the frame and the first scroll are compressed And a discharge port is formed so that the refrigerant is discharged toward the first space and the second space of the casing.

The frame may be provided with a discharge guide for guiding the refrigerant discharged from the discharge port to the second space separated from the first space.

A plurality of pin holes are formed in the second scroll, and a pin member constituting a rotation preventing portion of the second scroll can be fixedly coupled to the first scroll and the frame through the plurality of pin holes rotatably. have.

A plurality of protrusions protruding in the radial direction may be formed on the outer circumferential surface of the second scroll, and the pin holes may be formed in the plurality of protrusions.

In the electric compressor according to the present invention, since the bearing portion for supporting the rotary shaft in the radial direction is provided only at one side of the driving motor, the axial length of the compressor as a whole can be reduced as compared with the bearing portion formed at both ends of the rotary shaft.

In addition, since only one end of the rotary shaft is supported in the radial direction and the other end is free in the radial direction, the length of the rotary shaft projecting from the driving motor can be minimized. Accordingly, the inverter accommodating portion is arranged close to the drive motor, thereby increasing the possibility of contact between the inverter accommodating portion and the suction refrigerant, thereby effectively cooling the inverter.

Further, as the oil supply passage is formed in the rotary shaft, the length of the oil supply passage for supplying the oil to the respective bearings can be reduced, and the oil can be quickly supplied to the respective bearings during starting of the compressor, have.

Further, by supporting the rotary shaft in the radial direction by using the bush bearing, it is possible to reduce the cost due to the bearing, reduce the operation noise, and reduce the gap between the compression portion and the bearing, thereby reducing the refrigerant leakage in the compression chamber.

Further, since the compression chambers are formed on both sides of the orbiting scroll, the supporting force can be increased in the axial direction with respect to the orbiting scroll while eliminating the back pressure space, and the behavior of the orbiting scroll is stabilized, It can be suppressed effectively.

1 is a perspective view of a compressor module and an inverter module in an electric compressor according to an embodiment of the present invention,
FIG. 2 is a cross-sectional view of an internal structure of a compressor module and an inverter module in the electric compressor of FIG. 1,
Fig. 3 is a sectional view taken along the line IV-IV in Fig. 2, Fig. 4 is a sectional view showing the vicinity of the driving motor,
5 and 6 are views showing the rotating shaft, FIG. 5 is a sectional view showing the supporting state of the rotating shaft, FIG. 6 is a sectional view taken along line V-V in FIG. 5,
FIG. 7 is an enlarged sectional view of the compression mechanism in the electric compressor of FIG. 2,
8 is a plan view showing a state in which the stationary wrap and the orbiting wrap are engaged in the compression mechanism according to the present embodiment,
FIG. 9 is a sectional view of an electric compressor having a double-sided scroll according to the present invention, FIG.
FIG. 10 is an enlarged cross-sectional view showing the engaged state of the rotation preventing member in FIG. 9,
Fig. 11 is a sectional view for explaining the second scroll in Fig. 9,
12 is a sectional view showing a low-pressure scroll compressor to which a double-sided scroll is applied,
13 is a cross-sectional view showing another embodiment of a supporting structure of a rotating shaft in an electric compressor according to the present invention.

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 perspective view showing a compressor module and an inverter module in an electric compressor according to the present invention in an exploded manner. FIG. 2 is a cross-sectional view showing the compressor module and the inverter module assembled in the electric compressor according to FIG.

1, a low-pressure electric scroll compressor (hereinafter abbreviated as an electric compressor) 1 according to the present embodiment includes a compressor module 100 for sucking, compressing and discharging a refrigerant, a compressor module And an inverter module 200 detachably coupled to one side of the driving motor 103 to control the rotational speed of the driving motor 103 to be described later.

The compressor module 100 is provided with a first sealing terminal 107 and the inverter module 200 is provided with a second sealing terminal 201. The first sealing terminal 107 is exposed to the outside of the compressor module 100 so that the first sealing terminal 107 and the second sealing terminal 201 can be detached from each other and the second sealing terminal is exposed to the outside of the inverter module 200 As shown in FIG.

Meanwhile, the inverter module 200 is provided so as to be in contact with a portion of the compressor casing 101 constituting the suction space S1. Accordingly, heat generated in the inverter device 220 of the inverter module 200 and the like can be quickly dissipated by the coolant refrigerant sucked into the suction space S1.

In addition, the inverter module 200 includes an inverter housing 210 having a predetermined internal volume. At least one inverter element 220 for controlling the rotational speed of the drive motor 103 is housed in the inverter housing 210 as well as the second sealing terminal 201 described above.

The compressor module 100 includes a drive motor 103 serving as a motor and a compression mechanism 105 for compressing the coolant by using the rotational force of the drive motor 103 in the compressor casing 101.

The compressor casing 101 is provided with an intake port 111a to which the suction pipe is connected and an exhaust port 121a to which the discharge pipe is connected. The suction space S1 is connected to the suction port 111a, the discharge space S2 is provided to the discharge port 121a, Respectively. A drive motor 103 is installed in the suction space S1, and the compressor of the present embodiment is a low pressure compressor.

The compressor casing 101 includes a main housing 110 in which a driving motor 103 is installed and a rear housing 120 coupled to a rear end of the main housing 110. The inner space of the main housing 110 forms a suction space S1 together with one side of the compression mechanism 105 and the inner space of the rear housing 120 forms the discharge space S2.

The aforementioned exhaust port 121a is formed on one side of the rear housing main body 121 and is provided in the vicinity of the exhaust port 121a or around the exhaust port 121a to remove oil from the refrigerant discharged from the exhaust port 121a. A separator (not shown) may be installed. An oil separation portion S21 for separating oil from the refrigerant discharged from the compression chamber is formed in the upper half of the discharge space S2 and a low oil portion S22 for storing the oil separated in the discharge space S2 is formed in the lower half portion. May be formed. The low oil portion S22 is communicated with the compression mechanism portion 105 through the oil supply passage F0. The lubrication structure will be described later.

The main housing 110 has a cylindrical portion 111 formed in a cylindrical shape and a front end of the cylindrical portion 111 is integrally extended to form a closed portion 112. The rear end of the cylindrical portion 111 The opening 113 is formed. The inverter module 200 is coupled to the outer surface of the sealing part 112 and the compression mechanism 105 is coupled to the opening 113 to seal the suction space S1.

Here, the main housing 110 may have the same inner diameter as the front end and the rear end inner diameter. However, in consideration of the drawing of the mold core when the mold of the main housing 110 is manufactured, It is preferable to be formed larger than the inner diameter.

The enclosure 112 of the main housing 110 is formed with an inverter accommodating portion 115 that protrudes in a direction toward the opening 113 in the central portion of the inner surface thereof to form the inverter accommodating space S3. The inverter accommodating portion 115 is a space for accommodating the inverter radiating protrusions 211 of the inverter housing 210 and may be formed so as to be recessed at a height (or depth) that can overlap the intake port 111a in the radial direction. Accordingly, the contact area between the refrigerant sucked into the suction space S1 through the intake port 111a by the inverter housing part 115 and the sealing part 112 is increased, and the heat radiation effect for the inverter device can be enhanced . This will be described again while explaining the driving motor and the rotating shaft.

Meanwhile, a drive motor 103 constituting a motor-driven portion is press-fitted into the main housing 110. The driving motor 103 includes a stator 131 fixed to the inside of the main housing 110 and a rotor 132 positioned inside the stator 131 and rotated by the interaction between the stator 131 and the stator 131 .

The stator 131 is fixed to the inner circumferential surface of the main housing 110 by being shrunk. The outer circumferential surface of the stator 131 is formed to be D-cut so that a coolant passage is formed between the outer circumferential surface of the stator 131 and the inner circumferential surface of the compressor casing (hereinafter abbreviated as a casing) 110. The refrigerant sucked through the inlet port 111a can be guided to the compression chamber V through the suction groove 154 of the first scroll 150 to be described later.

The stator 131 is formed by laminating a plurality of thin annular steel plates to form a stator laminate 131a, and a coil 135 is wound around the stator laminate 131a. Fig. 3 and Fig. 4 are views for explaining the relationship between the intake port and the inverter accommodating portion, which are a sectional view taken along the line IV-IV in Fig. 2, and Fig. 4 is an enlarged sectional view around the drive motor.

3 and 4, the coil 135 is annular when viewed from the rear side, and the axial length L1 of the coil is longer than the axial length L2 of the stator laminate, The front end of the coil 135 facing the sealing portion 112 of the stator 110 protrudes from the front end of the stator laminate 131a. Accordingly, the inverter receiving portion 115 of the main housing 110 can be formed to have a height overlapping the intake port 111a in the radial direction and overlapping the coil 135 in the radial direction as described above. This is because the rotation shaft 133 to be described later is supported by the compression mechanism in the form of a cantilever so that it is not necessary to provide a separate subframe or bearing in the sealing portion 112 of the main housing 110, The inverter accommodating portion can be protruded to a height at which the inverter accommodating portion overlaps with the coil.

The rotor 132 is formed by stacking a plurality of thin annular steel plates like the stator 131 to form the rotor laminate 132a and the rotating shaft 133 is press-fitted to the inner circumferential surface of the rotor laminate 132a . The length of the rotor laminate is shorter than the length of the stator laminate, or at least shorter than the length of the coil.

The rotary shaft 133 is coupled to the center of the rotor 132 and has a rear end facing the compression mechanism 105 supported by a frame 140 and a fixed scroll 150 in a cantilevered manner.

2 and 4, the front end (second end) 133b of the rotating shaft 133 is formed to be shorter or equal to the front end of the rotor 132, and the rear end (first end) The fixed scroll 150 may be rotatably coupled to the fixed scroll 150 through the frame 140 and the orbiting scroll 160.

The front end 133b of the rotary shaft 133 may be longer than the front end of the rotor 132. However, since the front end of the rotary shaft 133 is formed as a free end that is not supported by a separate bearing, It need not be formed longer than the electron 132. It is preferable that the coil 135 is formed shorter than the front end of the coil 135 even if it is formed longer than the rotor. 5 and 6 are views showing rotation axes, FIG. 5 is a sectional view showing the supporting state of the rotation shaft, and FIG. 6 is a sectional view taken along line V-V in FIG.

5, since the first end 133a of the rotary shaft 133 is axially supported on the frame 140 and the fixed scroll 150 as described above and rotational force is transmitted to the orbiting scroll 160, The second bearing portion 133c2, the eccentric portion 133c3 and the first bearing portion 133c1 are formed in order from the first end portion 133a toward the second end portion 133b.

The first bearing portion 133c includes a first bush bearing 171 provided on the frame 140 and a second bearing portion 133c2 includes a second bush bearing 172 provided on the fixed scroll 150, The deep portion 133c3 is formed so as to correspond to the third bush bearing 173 provided in the orbiting scroll 160, respectively. Accordingly, the first bearing portion 133c1 and the second bearing portion 133c2 are formed on the coaxial center lines CL1 and CL2, and the eccentric portion 133c3 is formed on the first bearing portion 133c1 and the second bearing portion 133c2, And is formed on the other axial center line CL3 by eccentricity with respect to the portion 133c2.

The oil supply passage Fo for guiding the oil stored in the oil storing portion S22 to the bearing portions 133c1 and 133c2 and the eccentric portion 133c3 is formed on the rotary shaft 133. [ The oil supply passageway Fo has an oil supply groove 133e formed by a predetermined depth in a direction from the first end 133a of the rotary shaft 133 toward the second end 133b, 133f3, 133f2, and 133f3 that penetrate radially toward the bearing portions 133c1, 133c2 and the eccentric portion 133c3. The oil supply holes are formed by the first oil supply hole 133f1 corresponding to the first bearing portion 133c1, the second oil supply hole 133f2 corresponding to the second bearing portion 133c2, the third oil supply corresponding to the eccentric portion 133c3 And the hole 133f3, so that the respective oil supply holes can be formed within the axial range of the respective bearing portions and the eccentric portions corresponding to the oil supply holes.

On the other hand, a depressurizing portion may be formed in the oil supply groove 133e. That is, the inlet of the oil supply passage Fo is communicated with the discharge space (precisely the low oil portion) S2 which is the high pressure portion, while the outlet of the oil supply passage Fo is communicated with the suction space S1 which is the low pressure portion. Accordingly, the oil excessively flows out from the low oil portion S22 of the discharge space S2 into the suction space S1 or the oil of the refrigerant or the back pressure space S4 discharged into the discharge space S2 flows into the oil supply passage (Specifically, between the first bearing portion and the first bush bearing) to the suction space S1. 6, a pressure-reducing member 133g such as a pressure-reducing rod is inserted into the oil supply groove 133e to narrow the inner diameter of the oil supply groove 133e, so that the oil supply groove 133e passes through the pressure- It can be lowered to an intermediate pressure.

The rotary shaft 133 can be pushed toward the suction space S1 by the pressure difference between the discharge space S2 and the suction space S1. When the rotary shaft 133 is supported by the ball bearing, the rotary shaft 133 is supported in the axial direction by the ball bearing. When the rotary shaft 133 is supported by the bush bearing, the rotary shaft 133 is supported in the axial direction Thrust bearings shall be provided separately.

2 and 5, an axial bearing projection 136 may be formed on the rotary shaft 133 to be axially supported on the axial bearing surface 146 of the frame 140 . The axial bearing surface portion 146 of the frame 140 extends radially from the outer circumferential surface of the rotary shaft 133 and is formed into an annular flange shape, So as to protrude in the axial direction by a predetermined height from the end of the shaft hole 145 of the frame 140 forming the frame 140. [ Although not shown in the drawings, the balance weight 137 coupled to the rotating shaft may be axially abutted against the axial bearing surface portion 146 of the frame 140 to form a thrust bearing.

Meanwhile, in the scroll compressor according to the present embodiment, the orbiting scroll coupled to the rotary shaft is supported by the frame, and the compression mechanism is formed so as to form the compression chamber while pivotally moving relative to the fixed scroll. FIG. 7 is an enlarged cross-sectional view of the compression mechanism in the electric compressor of FIG. 2. FIG.

2 and 7, the compression mechanism 105 includes a frame 140, a fixed scroll (hereinafter referred to as a first scroll) 150 supported by the frame 140, a frame 140, And a revolving scroll (hereinafter referred to as a second scroll) 160 provided between the first scroll 150 and the second scroll 160.

The frame 140 is coupled to the front opening 113 of the main housing 110. The first scroll 150 is fixedly supported on the rear surface of the frame 140 and the second scroll 160 is engaged with the first And is pivotably supported on the rear surface of the frame 140 to pivot between the scroll 150 and the frame 140. The second scroll 160 is eccentrically coupled to the rotating shaft 133 coupled to the rotor 132 of the driving motor 103 and rotates relative to the first scroll 150, And a pair of compression chambers (V) formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber.

The frame 140 includes a frame rigid portion 141 formed in a circular plate shape and a frame side wall portion 141 protruding from the rear surface of the frame rigid portion 141 and coupled to the side wall portion 152 of the first scroll 150 142 are formed.

A frame thrust surface 143 is formed on the inner side of the frame side wall portion 142 and supported by the second scroll 160 to be axially supported. A part of the refrigerant is filled with the oil to form a back pressure space S4 supporting the back surface of the second scroll 160. [ Accordingly, the pressure in the back pressure space S4 forms an intermediate pressure between the pressure in the suction space S1 and the final pressure (i.e., the discharge pressure) of the compression chamber V. [

A frame shaft hole 145 through which the rotating shaft 133 passes is formed in the back pressure space S4 and a first bearing 171 is provided on the inner circumferential surface of the frame shaft hole 145. [

The first bearing 171 may be a bush bearing as shown in FIG. 5, but may be a ball bearing. However, since the bush bearing is less expensive than the ball bearing, it is advantageous in terms of cost as well as ease of assembly and weight and noise.

The back pressure space S4 includes a first sealing member 181 provided on the thrust surface between the frame 140 and the second scroll 160 and a second sealing member 182 disposed between the inner peripheral surface of the frame 140 and the outer peripheral surface of the rotary shaft 133 And can be sealed by the two sealing members 182.

The first sealing member 181 is formed in an annular shape having a rectangular cross section or a V (V) sectional shape and can be inserted into a first sealing groove (not shown) provided on the thrust surface 143 of the frame 140 have. In this case, the first sealing member 181 can be sealed with the second scroll 160 while being pushed up by the force of the pressure in the back pressure space S4.

The second sealing member 182 is formed in an annular shape having a U-shaped cross-sectional shape and can be inserted into an annular second sealing groove (not shown) provided around the frame shaft hole 145. In this case, the second sealing member 182 is opened by the force of the pressure in the back pressure space S4, and can seal the back pressure space S4 while closely contacting the outer circumferential surface of the rotation shaft 133. [ However, the second sealing member 182 may be omitted in some cases. When the second sealing member is excluded, the pressure in the back pressure space S4 is stagnated as the back pressure space S4 is communicated through the fine passage formed in the suction space S1 and the inner circumferential surface of the first bearing 171 So that oil can smoothly flow into each bearing hole.

Meanwhile, the first scroll 150 may be fixedly coupled to the frame 140 or may be press-fitted into the casing 110 to be fixed.

The first scroll 150 is formed in a substantially circular disk shape with a fixed scroll hard plate portion 151 and a side wall portion 142 of the frame 140 is formed at an edge of the first hard plate portion 151. [ (Hereinafter referred to as a first sidewall portion) 152 is formed. A fixed lap 153 (hereinafter referred to as a first lap) 153, which forms a compression chamber V, is formed on the front surface of the first rigid plate 151 so as to engage with a orbiting wrap (to be referred to as a second wrap hereinafter) The first lap 153 will be described later with the second lap 162.

A suction passage 154 is formed at one side of the first side wall portion 152 so that the suction space S1 and the suction chamber (not shown) are communicated with each other. In the central portion of the first hard plate portion 151, A discharge port 155 through which refrigerant is discharged into the discharge space S3 is formed. The discharge port 155 may be formed in only one of the first compression chamber V1 and the second compression chamber V2 so as to be communicated with the first compression chamber V1 and the second compression chamber V2, A first discharge port 155a and a second discharge port 155b may be formed so as to communicate with each other.

The bearing receiving portion 156 may protrude toward the inner wall surface of the rear housing 120 on the rear surface of the first hard plate portion 151. The bearing receiving portion 156 may be in close contact with the inner wall surface of the rear housing 120 or may be spaced apart by a predetermined distance. However, if the thickness of the first hard plate portion 151 can stably support the second bearing portion 133c2 of the rotary shaft 133, the bearing accommodating portion may not be formed.

However, when the bearing receiving portion 156 is formed, the oil feed pipe 157 protruding from the lowest point of the bearing receiving portion toward the bottom of the discharge space S2 may be connected. The internal space 156a of the bearing receiving portion 156 is connected to the low oil portion S22 of the discharge space S2 so that the oil filled in the low oil portion S22 is supplied to the bearing receiving portion 156 (Not shown).

The second bearing portion 133c2 of the rotating shaft 133 is rotatably inserted into the center of the bearing receiving portion 156 at the center of the first hard plate portion 151 so as to be radially supported. And a second bearing 172 is inserted and coupled to the second bearing hole 158. The second bearing 172 may be a bush bearing as shown in FIG. 5, but may be a ball bearing as in the case of the first bearing 171.

The second scroll 160 is provided between the frame 140 and the first scroll 150 and is rotatably coupled to the rotation axis 133 in an eccentric manner.

The second scroll portion 160 is formed in a substantially circular plate shape with the orbiting scroll plate portion 161 (hereinafter referred to as a second plate portion) 161, and is engaged with the first lap 153 on the rear surface of the second plate portion 161, A second wrap 162 forming a thread is formed.

The second wrap 162 may be formed in an involute shape with the first wrap 153, but may be formed in various other shapes. 8 is a plan view showing a state in which the stationary wrap and the orbiting wrap are engaged in the compression mechanism according to the present embodiment.

As shown in FIGS. 2 and 8, the second wrap 162 has a shape in which a plurality of arcs having different diameters and origin points are connected, and the outermost curve is formed in a substantially oval shape having a long axis and a short axis . This may also be done for the first wrap 153 as well.

A rotary shaft engaging portion 163 is formed on the central portion of the second hard plate portion 161 to form an inner end portion of the second lap 162 and to be described later and an eccentric portion 133c3 of the rotary shaft 133 is rotatably inserted, As shown in FIG. The outer circumferential portion of the rotary shaft coupling portion 163 is connected to the second wrap 162 to form the compression chamber V together with the first wrap 153 in the compression process.

The rotation axis connecting portion 163 is formed to have a height overlapping with the second lap 162 on the same plane so that the eccentric portion 133c2 of the rotation axis 133 overlaps the second lap 162 on the same plane As shown in FIG. As a result, the repulsive force and the compressive force of the refrigerant are canceled each other while being applied to the same plane with reference to the second longitudinal plate portion, so that the inclination of the second scroll 160 due to the action of the compressive force and the repulsive force can be prevented.

The rotary shaft engaging portion 163 is formed with a concave portion 163a to be engaged with the projection 153a of the first wrap 153 to be described later at an outer peripheral portion opposed to the inner end of the first wrap 153, An increase portion 163b is formed at one side of the portion 163a where the thickness from the inner peripheral portion to the outer peripheral portion of the rotary shaft coupling portion 163 increases on the upstream side along the forming direction of the compression chamber V. [ This makes the compression path of the first compression chamber (V1) just before discharge lengthened, and consequently the compression ratio of the first compression chamber (V1) can be increased close to the compression ratio of the second compression chamber (V2). The first compression chamber (V1) is a compression chamber formed between the inner surface of the first lap (153) and the outer surface of the second lap (162) and will be described later from the second compression chamber (V2).

On the other side of the concave portion 163a, an arc compression surface 163c having an arc shape is formed. The diameter of the arc compression surface 163c is determined by the inner end thickness of the first lap 153 (i.e., the thickness of the discharge end) and the turning radius of the second lap 162, Increasing the end thickness increases the diameter of the arc compression surface 163c. As a result, the thickness of the second wrap around the arc compression surface 163c also increases, so that the durability can be ensured and the compression path can be made long, so that the compression ratio of the second compression chamber V2 can be increased accordingly.

A protrusion 153a protruding toward the outer peripheral portion of the rotary shaft coupling portion 163 is formed near the inner end (suction end or start end) of the first lap 153 corresponding to the rotary shaft coupling portion 163, 153a may be formed with a contact portion 153b that protrudes from the projection and engages with the concave portion 163a. That is, the inner end of the first wrap 153 may be formed to have a larger thickness than the other portions. Accordingly, the lap strength at the inner end portion, which is subjected to the greatest compressive force among the first laps 153, can be improved and the durability can be improved.

On the other hand, the compression chamber V is formed between the first hard plate portion 151 and the first lap 153, and between the second lap 162 and the second hard plate portion 161, An intermediate pressure chamber, and a discharge chamber may be continuously formed.

8, the compression chamber V includes a first compression chamber V1 formed between the inner surface of the first lap 153 and the outer surface of the second lap 162, And a second compression chamber (V2) formed between the outer surface and the inner surface of the second wrap (162). That is, the first compression chamber (V1) includes a compression chamber formed between two contact points (P11, P12) formed by the inner surface of the first wrap (153) and the outer surface of the second wrap (162) And the second compression chamber V2 includes a compression chamber formed between two contact points P21 and P22 formed by the outer surface of the first wrap 153 and the inner surface of the second wrap 162 coming into contact with each other.

Here, the first compression chamber (V1) immediately before discharge has an angle (?) Having a larger value among the angles formed by the two lines connecting the center O of the eccentric portion, that is, the center O of the rotary shaft coupling portion and the two contact points P11 and P12 The distance l between the normal vectors at the two contact points P11 and P12 also has a value larger than zero.

This makes it possible to increase the size of the first lap 153 and the second lap 162 since the first compression chamber immediately before discharge has a smaller volume than when the first compression chamber has the fixed lap and the orbiting wrap made of the Invention Both the compression ratio of the first compression chamber (V1) and the compression ratio of the second compression chamber (V2) can be improved.

On the other hand, between the frame 140 and the second scroll 160, a rotation prevention mechanism for preventing the rotation of the second scroll 160 is provided. The anti-rotation mechanism may be an anti-blocking or pin-ring structure. The present embodiment will be described focusing on an example in which a pin-ring structure is applied.

The self-supporting portion 190 according to the present embodiment has the rotation preventing groove 191 formed on either the rear surface of the frame 140 or the front surface of the hard plate portion 161 of the second scroll 160, And a rotation preventing pin 192 that is rotatably inserted into the rotation preventing groove on the member facing the rotation preventing groove 191. [ 2 and 7 show an example in which the rotation prevention groove 191 is coupled to the frame 140 and the rotation prevention pin 192 is coupled to the second scroll 160, respectively.

The anti-rotation grooves 191 are formed at regular intervals along the circumferential direction outside the back pressure space S4 on the thrust surface 143 of the frame 140. [ The inner diameter of the rotation preventing groove 191 is larger than the rotation preventing pin 192 so that the rotation preventing pin 192 can rotate.

The rotation preventing groove 191 may be formed on the thrust surface 143 of the frame 140 as it is. However, after forming the annular groove (not shown) on the frame thrust surface 143, The rotation preventing grooves 191 may be formed at regular intervals.

The rotation prevention pins 192 and the rotation prevention grooves 191 are formed to correspond one to the other so that the rotation prevention pins 192 can be inserted into the plurality of rotation prevention grooves 191, respectively. Accordingly, the plurality of anti-rotation pins 192 are inserted into the respective anti-rotation grooves 191 to guide the rotation of the second scroll 160 while restricting the rotation of the second scroll 160.

Since the outer circumferential surface of the rotation prevention pin 192 continuously makes sliding contact with the inner circumferential surface of the rotation prevention groove 191, the rotation prevention groove 191 and the rotation prevention pin 192 are formed of a wear resistant material such as a spring steel . However, since the second scroll 160 and the frame 140, in which the anti-rotation grooves 191 and the anti-rotation pins 192 are formed, are formed of a light and soft material such as an aluminum material in consideration of the weight of the compressor, The preventing groove 191 and the rotation prevention pin 192 may be poor in wear.

The anti-rotation pin 192 is made of a material having high abrasion resistance and high rigidity such as a spring steel and is fixedly coupled to the second scroll 160. The anti-rotation pin 191 is formed of the same material as the rotation prevention pin 192 It is possible to form an anti-rotation mechanism having a pin-ring structure by inserting a lubricating ring made of a similar material.

Here, the lubricating rings may be individually formed and assembled, but a plurality of lubricating rings may be integrally formed by being bundled into an annular plate. This is also true of anti-rotation rings. That is, a plurality of anti-rotation rings may also be integrally formed on one annular plate and integrally joined to the second scroll.

Reference numerals 159a and 159b denote bypass holes.

The scroll compressor according to this embodiment operates as follows.

That is, when power is applied to the driving motor 103, the rotating shaft 133 rotates together with the rotor 132 to transmit rotational force to the second scroll 160.

Then, the second scroll (160) is pivoted by the anti-rotation mechanism, and the compression chamber (V) is continuously moved toward the center side, thereby reducing the volume.

2, the refrigerant flows into the suction space S1 through the inlet port 111a, and the refrigerant introduced into the suction space S1 flows to the outer circumferential surface of the stator 131 and the inner circumferential surface of the main housing 110 And is sucked into the compression chamber V through the passage formed or the gap between the stator 131 and the rotor 132 through the suction passage 154.

At this time, a part of the refrigerant sucked into the suction space S1 through the suction port 111a first comes into contact with the sealing part 112, which is the front surface of the main housing 110, before passing through the driving motor 103. [ Therefore, the sealed portion 112 is cooled by heat exchange with the cold suction refrigerant, thereby dissipating the heat of the inverter module attached to the outer surface of the main housing 110.

Particularly, when the inverter accommodating portion 115 provided in the closed portion 112 protrudes in the direction toward the drive motor 130 as in the present embodiment, the cold refrigerant sucked into the suction space S1 The heat dissipation effect of the closure part 112 can be enhanced and the temperature of the inverter housing 210 is lowered and the inverter elements 220 housed in the inverter housing 210 ) Can be released more quickly.

The refrigerant sucked into the compression chamber V through the suction space S1 is compressed by the first scroll 150 and the second scroll 160 and is discharged into the discharge space S2 through the discharge port 155 The refrigerant discharged to the discharge space S2 is separated from the discharge space S2 so that the refrigerant is discharged to the refrigeration cycle through the discharge port 121a while the oil is accumulated in the low oil S22.

The oil collected in the low oil portion S22 flows into the oil supply groove 133e of the rotary shaft 133 through the oil feed pipe 157 in accordance with the pressure difference between the discharge space S2 and the suction space S1, Is moved in the direction from the first end portion 133a of the rotating shaft 133 toward the second end portion 133b along the oil supply groove 133e so that the second oil supply hole 133f2 and the third oil supply hole 133f3, And is supplied to the oil supply hole 133f1. At this time, as the pressure reducing member 133g is inserted into the oil supply groove 133e, the pressure of the oil moving to the oil supply groove 133e is lowered to the intermediate pressure.

The oil supplied to the second oil supply hole 133f2 and the third oil supply hole 133f3 is moved to the compression chamber V and the back pressure space S4 according to the pressure difference so that the second bearing 172 and the third bearing The oil supplied to the first oil supply hole 133f1 lubricates the first bearing 171 while moving to the outer peripheral surface of the first bearing portion 133c1 in accordance with the pressure difference.

At this time, when the back pressure space S4 communicates with the suction space S1, the discharge space S2 is formed by the oil supply groove 133e of the rotating shaft 133 and the oil supply holes 133f1, 133f2, The back pressure space S4 and the suction space S1 are communicated with each other so that the oil is not stagnated in the low oil part S22, the oil supply passage Fo and the back pressure space S4, And the back pressure space S4 and the suction space S1, the respective bearing surfaces can be lubricated.

In this way, since the bearing portion for supporting the rotation shaft in the radial direction is provided only on one side of the drive motor with respect to the drive motor, the axial length of the compressor as a whole can be reduced.

In addition, since the rotary shaft does not protrude from the drive motor or the protruded length becomes shorter, the inverter accommodating portion can be disposed close to the drive motor, thereby increasing the possibility of contact between the refrigerant sucked into the suction space of the casing and the inverter accommodating portion. The inverter can be cooled effectively.

Further, since the oil supply passage is formed through the rotation shaft, the length of the oil supply passage can be reduced, and the oil can be quickly supplied during the start of the compressor, thereby reducing the friction loss.

Further, by supporting the rotary shaft in the radial direction by using the bush bearing, it is possible to reduce the cost due to the bearing, reduce the operation noise, and reduce the gap between the compression portion and the bearing, thereby reducing the refrigerant leakage in the compression chamber.

Further, as the rotary shaft is coupled through the orbiting scroll, the differential pressure between the back pressure of the back pressure space and the axial gas force in the compression chamber is reduced, whereby the behavior of the orbiting scroll is stabilized, Can be suppressed.

On the other hand, in the above-described embodiment, the double-sided scroll method in which the orbiting scroll of the orbiting scroll is formed only on one side of the orbiting scroll hard plate portion or the case where the orbiting wrap is formed on the front surface and the rear surface of the orbiting scroll hard- The same structure can be applied. FIG. 9 is a sectional view showing an electric compressor having a double-sided scroll according to the present invention.

As shown in the drawing, the second scroll 1160, which is the orbiting scroll, is formed with first and second orifices 1162a and 1162b on both sides in the axial direction of the long plate portion 1161, A first fixed wraps 1153 may be formed on the first scroll 1150 corresponding to the second wraps 1162a and a second fixed wraps 1147 may be formed on the frame 1140 corresponding to the second wraps 1162b . Accordingly, the first or second orifices 1162a and 1162b are engaged with the first or second orifices 1145 and 1157 to form the first compression space Vc1 or the second compression space Vc2, (Vc2). Since the first compression space Vc1 and the second compression space Vc2 form the first compression chamber and the second compression chamber, respectively, the electric compressor of the double-side scroll type forms four compression chambers.

In this case, the intake port 1111a is formed to pass between the side wall portion of the main housing 110 and the frame 1140 constituting the compressor casing and the side wall portion of the first scroll 1150, and the intake port 1111a is formed in the frame 1140 and the first scroll 1150 in the compression space Vc1 (Vc2). Accordingly, the outlet end of the intake port 1111a may be formed so as to face the first compression space Vc1 and the second compression space Vc2 corresponding to the hard plate portion of the second scroll 1160. [

A first discharge port 1155 is formed in the first longitudinal plate portion 1151 of the first scroll 1150 and a second discharge port 1148 is formed in the frame longitudinal plate portion 1141 of the frame 1140, The refrigerant compressed in the compression space Vc1 flows through the first discharge port 1155 and the refrigerant compressed in the second compression space Vc2 flows through the second discharge port 1148 into the inner space of the rear housing 1120, And is discharged into the inner space of the housing (1110). The refrigerant discharged to the inner space of the main housing passes through the side wall of the frame 1140 and the side wall of the first scroll 1150 and moves to the inner space of the rear housing 1120, And is discharged to the outside. Accordingly, the scroll compressor of the present embodiment forms a high-pressure scroll compressor in which the entire inner space of the casing 1101 forms a kind of discharge space.

The first end portion 1133a of the rotary shaft 1133 passes through the frame 1140, the second scroll 1160 and the first scroll 1150 in order, 1 scroll 1150 and the second end portion 1133b of the rotation shaft 1133 is coupled to the rotor 1132 to form a free end. Accordingly, the inverter accommodating portion 1115 is protruded toward the driving motor in the sealing portion 1112 on the front side of the main housing 1110, which is the same as the above-described embodiment. Although not repeatedly described, the basic structure including the bearings and the operation and effects thereof are the same as those of the above-described embodiment.

However, since the compression spaces are formed on both sides of the orbiting scroll in this embodiment, it is not necessary to form a separate back pressure space, and the structure of the compression mechanism can be simplified accordingly. As a result, the axial support force for the orbiting scroll becomes constant, and the behavior of the orbiting scroll becomes more stable, so that high-speed operation becomes possible and the refrigerant leakage can be effectively suppressed.

In this embodiment, since the first revolving lap 1162a and the second revolving lap 1162b are formed on both sides of the second scroll 1160, the rotation preventing member 1190 is formed to be positioned within the range of the orbiting wrap It is difficult to do. Accordingly, in the present embodiments, the rotation preventing member can be formed outside the range of the orbiting wrap. 10 is a cross-sectional view showing an enlarged view of the engaged state of the rotation preventing member in FIG.

A plurality of pin fixing grooves 1191a and 1191b are formed at predetermined intervals in the frame side wall portion 1142 of the frame 1140 and the first side wall portion 1152 of the first scroll 1150 as shown in Fig. And a plurality of pin holes 1192 are formed in the second scroll 1160 so as to correspond to the respective pin fixing grooves 1191a and 1191b. A lubricating ring 1192a may be inserted into the pin hole 1192. [

One end of the pin member 1193 is first inserted into one of the pin fixing grooves 1191a and 1191b of the frame side wall portion 1142 or the first side wall portion 1152, The other end passes through the pin hole 1192 and is later inserted into the other pin fixing groove, so that both ends of the pin member 1193 are fixedly coupled. The diameter of the pin member 1193 is formed smaller than the inner diameter of the pin hole 1192. [ The pin member 1193 is rotatably inserted into the pin hole 1192 of the second scroll 1160 in a state where the pin member 1193 is inserted and fixed to the side wall portions 1142 and 1152. In this state, Thereby suppressing the rotating motion of the rotor 1160 and inducing the turning motion.

As the pin hole 1192 is formed at the edge of the second hard plate portion 1161, the outer diameter of the second hard plate portion 1161 increases and the second scroll 1160 may become heavy. Then, the load of the driving motor is increased, and the compressor efficiency may be lowered. Fig. 11 is a sectional view for explaining the second scroll in Fig. 9; Fig.

11, a plurality of radial protruding portions 1165 are formed on the rim surface of the second hard plate portion 1161 at regular intervals along the circumferential direction, and the radial protruding portion 1165 is formed with the pin hole 1192, Respectively. Accordingly, the diameter of the second scroll may increase while the weight of the second scroll may not increase significantly.

Although not shown in the drawing, a rotation prevention pin may be fixed to the second scroll, and a rotation preventing groove serving as a pin hole may be formed in the frame and the first scroll.

When the rotation of the second scroll is suppressed by using the pin and the ring in the double-sided scroll compressor, the pin member can serve as a reference pin for setting the assembly position of the frame and the first scroll, The pin and the reference groove can be excluded.

Meanwhile, although the high-pressure type compressor in which the double-sided scroll is applied has been described in the above embodiment, the double-sided scroll can also be applied to the low pressure type compressor. 12 is a sectional view showing a low-pressure scroll compressor to which a double-sided scroll is applied.

As shown in Fig. 12, a frame (in the case of the double-sided scroll compressor according to the present embodiment, of course, a frame and a first scroll (not shown) are provided so as to separate the internal space of the casing 1101 into the suction space S1 and the discharge space S2. The refrigerant discharged from the second compression space Vc2 is supplied to the discharge space S2 (i.e., the second discharge space S1), which is the opposite side, So that the low-pressure scroll compressor can be formed even in the double-sided scroll compressor.

A refrigerant passage Fc communicating between the suction space S1 and the discharge space S2 is formed in the frame 1140 and the first scroll 1150 and the discharge guide 1149 is connected to the second discharge port 1148 and the refrigerant passage Fc. The refrigerant discharged through the second discharge port 1148 moves to the discharge space S2 through the discharge guide 1149 and the refrigerant passage Fc and is discharged from the first compression space Vc1 to the discharge space S2 The refrigerant flows to the exhaust port 1121a.

In the case of the low-pressure scroll compressor to which the double-sided scroll is applied as described above, the basic structure and operation effects are the same as those of the high-pressure scroll compressor described above.

In the above embodiments, the third bearing portion of the rotary shaft is rotatably coupled to the first scroll and is supported in the radial direction. However, the third bearing portion of the rotary shaft is rotatably inserted into the bearing receiving portion provided in the rear housing. And may be supported in the radial direction. 13 is a cross-sectional view showing another embodiment of a supporting structure of a rotating shaft in the electric compressor according to the present invention.

13, a bearing protrusion 1122 is formed on the inner peripheral surface of the rear housing 1120 in a direction toward the first scroll 1150, and a frame 1140 and a second The bearing 1122a is formed such that the first end 1133a of the rotary shaft 1122 passing through the scroll 1160 and the first scroll 1150 is rotatably engaged.

A second bearing 1172 made of a bush bearing can be inserted and coupled to the inner circumferential surface of the bearing groove 1122a to radially support the second bearing portion 1133c2 of the rotation shaft 1133. [

A sealing member 1123 is provided between the end surface of the bearing groove 1122a and the rear surface of the first scroll 1150 so that the refrigerant in the discharge space S2 flows into the compression chamber V or the inside of the bearing groove 1122a It is possible to block the inflow into the space.

The basic structure of the electric compressor according to the present embodiment as described above, and the operation and effect thereof are the same as those of the above-described embodiment. However, since the second bearing 1172 supporting the second bearing portion 1133c2 of the rotary shaft 1133 is installed in the casing 1110 instead of the first scroll 1150, And the first scroll 1150 can be prevented from being thermally deformed due to friction with the rotating shaft 1133 even if the rotating shaft 1133 rotates at a high speed, It is possible to increase the reliability.

Although not shown in the drawings, in the case of the present embodiment, the second scroll can be applied to the double-sided scroll. In this case as well, the basic configuration described above can be applied equally.

100: compressor module 101: compressor casing
111: Cylindrical portion 111a:
112: sealing part 115: inverter receiving part
120: rear housing 121a: exhaust port
103: drive motor 131: stator
131a: stator laminate 132: rotor
132a: rotor laminate 133: rotating shaft
133a, 133b: first and second end portions 133c1, 133c2: first and second bearing portions
133c3: eccentric portions 133f1, 133f2, 133f3: first, second,
133g: pressure reducing member 135: winding coil
136: Axial bearing part 137: Balance weight
140: frame 141:
142: frame side wall portion 145: frame soccer yoke
146: axial bearing surface part 150: fixed scroll (first scroll)
151: first hard plate part 152: first side wall part
153: stationary wrap (first wrap) 155: discharge port
156: bearing receiving portion 160: orbiting scroll (second scroll)
161: second hard plate portion 162: second wrap
163: rotation shaft coupling portion 171,172,173: first, second and third bearings
190: a front portion 191: a rotation preventing groove
192: anti-rotation pin 200: inverter module
210: inverter housing 220: inverter element

Claims (17)

A casing having a sealed inner space;
A first scroll fixed radially in an inner space of the casing;
A second scroll that forms a pair of two compression chambers between the first scroll and the first scroll, while being pivotally engaged with the first scroll;
A frame fixed in a radial direction opposite to the first scroll with the second scroll interposed therebetween;
A driving motor provided on the opposite side of the second scroll with the frame therebetween; And
The first end being a fixed end passing through the frame, the second scroll, and the first scroll and being radially supported by the first scroll and the frame, and a second end, opposite the first end, And an end portion coupled to the rotor of the driving motor to form a free end,
Wherein the driving motor has a stator surrounding the rotor coupled to the casing, a winding coil wound around the stator,
The second end of the rotating shaft is formed such that an end thereof is located within an axial range of the winding coil,
One side of the casing protrudes toward the drive motor to form an inverter accommodating portion,
Wherein at least a part of an inverter housing accommodating an inverter element is inserted into the inverter accommodating portion,
And at least a part of the inverter accommodating portion is formed to be positioned within the range of the winding coil. delete delete delete The method according to claim 1,
An inner space of the casing is formed with an air inlet so that a suction pipe communicates with a space where the driving motor is provided with respect to the frame,
Wherein at least a part of the inverter accommodating portion is formed in a range where the inverter accommodating portion overlaps with the intake port in a radial direction. The method according to claim 1,
A first bearing portion and a second bearing portion are formed on both sides of the eccentric portion in the axial direction of the eccentric portion,
Wherein the first bearing portion and the second bearing portion are formed to have coaxial center lines, and the eccentric portion is formed to have a different axial center line from the first bearing portion or the second bearing portion. The method according to claim 6,
And a bearing receiving protrusion protruding toward the casing to receive the second bearing portion of the rotating shaft is formed in the first scroll. The method according to claim 6,
And a bearing receiving recess portion protruding toward the first scroll and receiving the second bearing portion of the rotating shaft is formed in the casing. The method according to claim 6,
Wherein at least one of the first bearing portion and the second bearing portion is supported by a bush bearing. The method according to claim 1,
Wherein the rotary shaft has an oil supply groove formed at an end of the first end portion to a predetermined length in the axial direction,
Wherein a plurality of oil supply holes are formed in the oil supply groove so as to face the respective bearing portions and the eccentric portion with an interval along the axial direction. 11. The method of claim 10,
Wherein the oil supply groove is provided with a pressure reducing member for reducing pressure of the oil. The method according to claim 1,
Wherein the second scroll is formed with a swinging lap at one side thereof in contact with the first scroll, and a rotation axis coupling portion is formed at a central portion of the swinging lap,
A back pressure space is formed between the second scroll and the frame, and the pressure of the back pressure space forms an intermediate pressure between the internal space pressure of the casing and the final pressure of the compression chamber. The method according to claim 1,
Wherein the first scroll and the second scroll are engaged with the first or second orifice and the second orifice to form a compression chamber, respectively, in the first scroll and the frame, Wherein the fixed lap and the second fixed lap are formed. 14. The method of claim 13,
The inner space of the casing is divided into a first space where the driving motor is provided and a second space opposite to the first space with respect to the frame,
Wherein the discharge port is formed in the frame and the first scroll such that the refrigerant compressed in the compression chambers is discharged toward the first space and the second space of the casing. 15. The method of claim 14,
Wherein the frame is provided with a discharge guide for guiding the refrigerant discharged from the discharge port to the second space separated from the first space. 14. The method of claim 13,
Wherein a plurality of pin holes are formed in the second scroll, and a pin member constituting a rotation preventing portion of the second scroll is fixedly coupled to the first scroll and the frame through the plurality of pin holes rotatably. An electric compressor. 17. The method of claim 16,
A plurality of protrusions protruding in the radial direction are formed on an outer peripheral surface of the second scroll,
And the pin holes are formed in the plurality of projections.

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