KR101907950B1 - Motor operated compressor - Google Patents

Abstract

An electric compressor according to the present invention includes: a first scroll; 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; And a plurality of rotation preventing pins provided on the side opposite to the first scroll with the second scroll interposed therebetween and in contact with the second scroll, A frame formed along the frame; And a plurality of ring portions extending in a circumferential direction and protruding in a direction toward the surface provided with the pin groove are formed in the plate portion, and the plurality of ring portions are inserted into the plurality of pin grooves And an annular plate.

Description

[0001] MOTOR OPERATED COMPRESSOR [0002]

The present invention relates to a compressor, and more particularly to an electric compressor 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. In this scroll-type electric compressor, a rolling section of a rotary motor is provided inside a closed casing, a pressure concentric shaft formed by a fixed scroll and an orbiting scroll is installed on one side of the rolling section, The rotational force of the east is transmitted to the plunger. The rotating force transmitted to the plunger shaft causes the orbiting scroll to pivot relative to the fixed scroll to form a pair of two compression chambers composed of a suction chamber, an intermediate pressure chamber and a discharge chamber. The refrigerant is sucked into both compression chambers, .

In the electric compressor, a constant-speed compressor having a constant operation speed by applying a constant-speed motor has been mainly known. Recently, an inverter-type compressor capable of varying the operation speed of the motor to meet various consumer demands has been widely introduced . 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.

In addition, an electric compressor can be divided into a high-pressure type and a low-pressure type according to a method of sucking refrigerant. The high-pressure type is a method in which the refrigerant is directly sucked into the compression chamber, and the low-pressure type is a method in which the refrigerant is indirectly sucked into the compression chamber.

Accordingly, in the high pressure type compressor, the refrigerant compressed in the compression chamber is discharged to the inner space of the casing having the electric drive portion, and the refrigerant passes through the inner space of the casing and the refrigerant and oil are separated, While the refrigerant is discharged to the outside of the compressor through the exhaust port. Since the internal space of the high pressure type compressor forms a kind of oil separation space, it is possible to prevent the oil from being mixed with the refrigerant and flowing out.

On the other hand, in the low-pressure type compressor, the refrigerant is sucked into the compression chamber through the inner space of the casing having the transmission portion, and the refrigerant is discharged to the outside of the compressor directly through the discharge space. The refrigerant and the oil may be discharged to the outside of the compressor together. In view of this, there is conventionally known a technique of installing a centrifugal oil separator in an exhaust port and centrifugally separating oil from the refrigerant discharged. In some cases, such a centrifugal oil separator is applied even in a high-pressure type.

However, in the conventional electric compressor as described above, a plurality of switching elements constituting the inverter or the printed circuit board are coupled to the casing, thereby complicating the assembling process. That is, the housing constituting the casing must be fastened to another housing constituting the casing in a state where various components constituting the inverter are assembled to the housing. Therefore, the components constituting the inverter in the process of assembling the plurality of housings may be detached or damaged from the housing in which the components are mounted, so that it is very difficult to assemble the housing. In addition, when the components constituting the inverter are mounted on the housing, the housing itself must be replaced or removed when the inverter is replaced, so that replacement or maintenance work of the inverter may become difficult.

In addition, in the conventional electric compressor, when the centrifugal oil separator is applied, the number of components increases due to the installation of the centrifugal oil separator, which increases the manufacturing cost of the electric compressor. In addition, the centrifugal oil separator has a problem in that the oil separation efficiency is low due to a narrow space in which the oil is separated, thereby increasing the amount of the oil flowing out together with the refrigerant.

In addition, in the conventional electric compressor, since the rear side of the main housing constituting the casing is formed in a partially clogged structure, the core of the mold is taken out to the front side opened when the main housing is manufactured. Accordingly, the inner circumferential surface of the main housing is formed with an inner diameter on the front side larger than an inner diameter on the rear side so that the core of the mold can be easily taken out. However, this is because the thickness of the main housing is thicker than the thickness of the front side which is opened when the main housing is closed, which causes a delay in the hardening time of the thicker rear side compared to the thin front side of the main housing, . This causes a difference in strain rate between the front side and the rear side of the main housing, which causes an increase in assembly error when assembling components such as another housing or a stator. In addition, since the thickness of the rear side of the main housing is increased, the weight of the casing increases to increase the weight of the compressor as a whole, and the compressor also interferes with other members.

In the conventional electric compressor, a pin-and-ring unit is applied as a rotation preventing mechanism for causing the orbiting scroll to pivot relative to the fixed scroll. However, in the conventional pin-ring unit, since a plurality of rings are formed individually, there has been a problem in that the cost of the material increases and the cost of the assembly increases. In addition, in such a single pin-ring structure, the frame made of the same material and the orbiting scroll face each other, leading to an increase in friction loss and wear. In addition, in such a single pin-ring structure, a sealing groove is formed in a frame facing the orbiting scroll to form a back pressure chamber therein, and an annular sealing member is inserted into the sealing groove. However, The formation of the back pressure chamber is delayed due to the delay of the lifting of the sealing member as well as the increase in the material cost, thereby causing leakage of the compression chamber.

In addition, in the conventional electric compressor, since the back pressure chamber is sealed to form a kind of stagnation pressure, the oil is not smoothly supplied to the back pressure chamber and oil shortage occurs in the back pressure chamber, There is a problem that frictional loss is generated. In other words, conventionally, a back pressure hole is formed in the orbiting scroll, and a part of the refrigerant compressed in the intermediate pressure chamber or the discharge chamber flows into the back pressure chamber. By the refrigerant of the intermediate pressure or discharge pressure flowing into the back pressure chamber, Thereby forming a back pressure for supporting in a direction. However, when the back pressure chamber forms the stagnation pressure, the pressure difference between the intermediate pressure chamber or the discharge chamber and the back pressure chamber is not equal or similar, so that the refrigerant of the intermediate pressure or the discharge pressure can not be introduced into the back pressure chamber. As a result, the amount of oil that moves from the compression chamber to the back pressure chamber together with the refrigerant sharply decreases, so that the sealing member or the bearing member provided in the back pressure chamber can not be lubricated, resulting in a reduction in reliability due to friction loss or wear. In addition, there is a problem in that oil supply to other sliding portions supporting the rotating shaft is also insufficient, resulting in an increase in frictional loss as a whole or wear of parts constituting the sliding portion is increased.

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

It is an object of the present invention to provide an electric compressor capable of easily assembling an inverter in a casing.

Another object of the present invention is to provide an electric compressor capable of easily replacing or repairing an inverter without replacing or removing the casing.

Another object of the present invention is to provide an electric compressor in which the centrifugal oil separator is eliminated to reduce the number of parts and to secure a wide oil separation space so that oil can be effectively prevented from flowing out together with the refrigerant.

Another object of the present invention is to provide an electric compressor in which a casing can be easily manufactured, but also a casing can be prevented from being deformed and a weight can be reduced.

Another object of the present invention is to provide an electric compressor in which the anti-rotation mechanism of the orbiting scroll having a pin-ring structure is modularized to facilitate manufacture and assembly, thereby reducing manufacturing cost.

Another object of the present invention is to provide an electric compressor capable of easily forming a back pressure space using a pin-ring structure.

Another object of the present invention is to provide an electric compressor in which the sealing force of the back pressure space is increased to improve the back pressure effect and at the same time, the internal pressure of the back pressure chamber is made fluid pressure so that oil can be smoothly supplied.

Another object of the present invention is to provide an electric compressor in which oil can be smoothly supplied to the sliding portion on the opposite side of the rotating shaft.

In order to accomplish the object of the present invention, there is provided a compressor comprising: a compressor module for compressing a refrigerant and a compressor module for accommodating a motor for driving the compression mechanism; An inverter module provided at one side of the compressor module outside the compressor module and electrically connected to the driving unit to control the number of revolutions of the driving unit; A first sealing terminal provided in the compressor module and having a terminal exposed to the outside; And a second sealing terminal provided on the inverter module, the second sealing terminal being detachable from the terminal of the first sealing terminal by exposing the terminal to the outside.

Here, the compressor module includes a compressor casing accommodating the compression mechanism and the transmission unit, and the compressor casing is provided with a suction space through which the suction pipe communicates, and the inverter module may be provided in contact with a portion of the suction space have.

The compressor casing is provided with a first housing in which the suction space is formed, and a second housing is provided at one side of the first housing with a compression mechanism interposed therebetween to form a discharge chamber between the compressor housing and the compressor housing The second housing is formed with an exhaust port connected to a discharge pipe and the end of the exhaust port in contact with the discharge chamber may be formed higher than the inner surface of the second housing constituting the discharge chamber.

The compressor casing includes: a first housing having one end open and the power transmission unit fixed; And a second housing coupled to an opening side of the first housing, wherein an opening-side end portion of the first housing and an end portion of the second housing portion corresponding to the opening-side end portion are inserted into the other end portion, And a stepped surface is formed so that the stepped surface is coupled to the end surface of the counterpart end so as to face in the axial direction, and the end surface of the stepped surface is inserted in the radial direction The first portion and the second portion facing each other in the axial direction may be respectively provided with a sealing member.

The compressor casing includes: a first housing having one end opened and a second end formed in a clogged shape to fix the motor-driven portion; And a second housing coupled to an opening end of the first housing such that the first housing has a gradient angle in which an inner diameter and an outer diameter of each of the first and second housings are expanded toward the opening end, .

The compression mechanism includes: a frame supporting the rotation shaft; A first scroll supported on the frame; And a second scroll disposed between the frame and the first scroll and coupled to the rotation axis to form a pair of two compression chambers between the frame and the first scroll, A back pressure space for supporting the second scroll in the first scroll direction is formed between the first scroll and the second scroll facing the first scroll, and a discharge hole for discharging the pressure of the back pressure space to the suction space of the casing is formed in the rotation shaft .

In order to achieve the object of the present invention, the first scroll; 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; And a plurality of rotation preventing pins provided on the side opposite to the first scroll with the second scroll interposed therebetween and in contact with the second scroll, A frame formed along the frame; And a plurality of ring portions extending in a circumferential direction and protruding in a direction toward the surface provided with the pin groove are formed in the plate portion, and the plurality of ring portions are inserted into the plurality of pin grooves And an annular plate (40).

Here, the annular plate may have a sealing surface portion formed on the opposite surface of the surface on which the ring portion is formed, and the sealing surface portion may be formed by annularly protruding toward the surface provided with the rotation prevention pin.

At least one or more oil through holes may be formed in the sealing surface portion.

The annular plate may have an annular recess formed in a surface opposite to the surface on which the annular portion is formed, and an annular sealing member may be inserted into the annular groove.

An annular groove may be formed in the frame, and the annular plate may be inserted into the annular groove.

The depth of the annular groove may be greater than or equal to the thickness of the annular plate.

A fixing hole is formed on the outer circumferential surface of the annular plate so as to extend to the contact surface between the first scroll and the frame. A reference hole is formed in the fixing hole so that the reference pin passing through between the first scroll and the frame passes through the hole. .

The annular plate may be formed of a material different from that of the second scroll or the frame.

The annular plate may be formed of a material having a higher rigidity than the second scroll or the frame.

The annular plate may have a coating surface formed on the surface thereof with a material different from that of the second scroll or the frame.

The coating surface may be formed of a material having a higher rigidity than the second scroll or the frame.

In order to achieve the object of the present invention, the first scroll; 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; And a plurality of rotation preventing pins provided on the side opposite to the first scroll with the second scroll interposed therebetween and in contact with the second scroll, A frame formed along the frame; And an annular plate is formed in an annular shape, and a plurality of ring portions penetrating along the circumferential direction are formed in the plate portion, and the plurality of ring portions include an annular plate corresponding to the plurality of pin grooves. Can be provided.

Here, the outer circumferential surface of the annular plate is provided with a fixing protrusion extending to the contact surface between the first scroll and the frame, and a reference hole is formed in the fixing protrusion so that the reference pin penetrating between the first scroll and the frame passes through .

INDUSTRIAL APPLICABILITY According to the electric compressor of the present invention, since the compressor module and the inverter module are detachable, the inverter can be easily assembled to the compressor casing constituting the compressor module.

In addition, since the inverter module can be separated from the compressor module without replacing or removing the compressor casing, replacement or repair work of the inverter can be facilitated.

In addition, by applying the collision type oil separator to separate the oil from the refrigerant discharged from the compression mechanism of the compressor module, the centrifugal type oil separator is eliminated to reduce the number of parts and to secure a wide oil separation space, It is possible to effectively suppress leakage.

In addition, since the compressor casing is formed to have an inner gradient and an outer gradient, the compressor casing can be easily manufactured, and the portion where the thickness difference of the compressor casing is generated is minimized to prevent deformation and reduce the weight.

It is another object of the present invention to provide an electric compressor in which the anti-rotation mechanism of the orbiting scroll is modularized to facilitate manufacture and assembly by forming an integral pin-ring structure in which a plurality of ring portions are integrated.

Further, a back pressure space can be easily formed by replacing the back pressure forming member with a part of the annular plate having an integral pin-ring structure or by fitting the back pressure forming member to the annular plate.

In addition, by using the rotary shaft to communicate the inside of the back pressure space with the suction space, the inside of the back pressure space forms the flow pressure and the refrigerant and the oil flow smoothly through the back pressure space, Can be lubricated.

In addition, since the discharge hole is formed in the rotary shaft and the area of the discharge hole is formed to be extended to the bearing supporting the other end of the rotary shaft, the refrigerant that has been reduced in pressure while passing through the discharge hole smoothly flows to the sliding portion on the opposite side of the rotary shaft, .

1 is a perspective view showing a compressor module and an inverter module separated from each other in an electric compressor according to the present invention,
FIG. 2 is a perspective view showing a compressor module and an inverter module assembled in the electric compressor of FIG. 1,
Fig. 3 is a sectional view taken along the line "IV-IV" in Fig. 2, and is a longitudinal sectional view showing the inside of the electric compressor,
Fig. 4 is a front view of the compressor module seen from the front side in Fig. 1,
5A and 5B are cross-sectional views taken along the line "V-V" in Fig. 4,
Fig. 6 is a perspective view of the compressor casing seen from the rear side in Fig. 1,
Fig. 7 is a sectional view taken along the line "VI-VI" in Fig. 6,
Figs. 8A and 8B are enlarged cross-sectional views of the "A" part of Fig. 7, showing embodiments of a compressor casing and a stator support,
Fig. 9 is a vertical sectional view of the rear housing of the compressor module shown in Fig. 3,
Fig. 10 is a front view of the rear housing viewed from the front side in Fig. 9,
11 is a cross-sectional view taken along the line "VII-VII" in Fig. 10,
12A and 12B are front views showing embodiments of the second oil separator in FIG. 10,
Fig. 13 is a front view of the non-orbiting scroll shown in Fig. 9,
FIG. 14 is a longitudinal sectional view showing the compression mechanism of the compressor module shown in FIG. 3,
FIG. 15 is a perspective view showing a part of the compression mechanism part in explaining an embodiment of the anti-rotation mechanism in FIG. 14,
FIG. 16 is a perspective view of a part of the compression mechanism shown in FIG. 15,
17 is a sectional view taken along line "VIII-VIII" in Fig. 16,
Fig. 18 is an assembled longitudinal sectional view showing another embodiment of the anti-rotation mechanism in Fig. 14. Fig.
19 and 20 are an exploded perspective view and an assembled longitudinal sectional view showing another embodiment of the anti-rotation mechanism in Fig. 14. Fig.
Fig. 21 is an assembled longitudinal sectional view showing another embodiment of the anti-rotation mechanism in Fig. 14,
Fig. 22 is a longitudinal sectional view showing the compression mechanism and the rolling section of the compressor module in Fig. 3,
Fig. 23 is a perspective view showing a part of the rotating shaft broken in Fig. 22,
24A and 24B are cross-sectional views taken along the line "IX-IX" in Fig. 23,
FIG. 25 is a schematic view for explaining a structure in which the discharge hole and the pin hole communicate with each other in FIG. 23;
FIG. 26 is a longitudinal sectional view showing another embodiment of the pin hole in FIG. 25;
FIG. 27 is a vertical sectional view showing a bearing support portion to which a front end of a rotary shaft is coupled in FIG. 22;
FIG. 28 is a longitudinal sectional view showing another embodiment of the discharge hole in FIG. 22;
Fig. 29 is a schematic view for explaining a process in which oil is circulated together with refrigerant from the back pressure space to the suction space in the compressor according to Fig. 22; 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 perspective view showing a compressor module and an inverter module separated from each other in an electric compressor according to the present invention, FIG. 2 is a perspective view showing a compressor module and an inverter module assembled in the electric compressor according to FIG. 1, Sectional view taken along the line "IV-IV" and showing the inside of the electric compressor.

As shown in these drawings, a low-pressure electric scroll compressor (hereinafter abbreviated as a scroll compressor) 1 according to the present embodiment includes a drive motor 103, which is a motorized part, A compressor module 100 provided with a compression mechanism 105 for sucking, compressing and discharging the refrigerant by using the rotational force of the motor 103; a driving motor 103 detachably coupled to one side of the compressor module 100, And an inverter module 200 for controlling the rotational speed of the motor.

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.

An intake port 111a is formed at one side of the compressor casing 101 and connected to a suction pipe (not shown) to guide the refrigerant to the compression mechanism section 105. The other end of the compressor casing 101 is compressed And an exhaust port 121 through which a discharge pipe (not shown) is connected to discharge the refrigerant is formed.

The intake port 111a is formed so as to communicate with the internal space of the compressor casing 101 in which the drive motor 103 is installed so that the internal space of the casing 101 in which the drive motor 103 is installed is connected to the suction space S1, . Accordingly, the compressor of the present embodiment becomes a low-pressure compressor.

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, the heat generated in the switching device 220 of the inverter module 200 and the like can be rapidly dissipated by the cool coolant 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 switching 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 switching element 220 may be completely housed inside the inverter housing 210. However, this may be disadvantageous for effectively dissipating the heat generated in the switching element 220. [ Thus, a device exposure hole 211 is formed on one side of the inverter housing 210, more precisely on the side in contact with the compressor casing 101. Through this device exposure hole 211, It may be advantageous for the heat radiating side to allow one end to be exposed to the outside.

The end of the exposed switching element 220 is arranged so as to be in proximity to or in contact with the outer surface of the portion constituting the suction space S1 of the compressor casing 101, Can be advantageous. A heat dissipation pad (not shown) may be provided between the exposed surface of the switching element 220 and the outer surface of the corresponding sealing portion 112 to enhance the heat dissipation effect.

Here, as the switching element is supported on the printed circuit board at one end and the free end is at the other end, the free end thereof may be supported using a compressor casing. Figs. 4 to 5B are a front view and a longitudinal sectional view showing embodiments thereof.

4, the element seating groove 112b may be formed such that the end of the switching element 220 is inserted and supported on the outer surface of the compressor casing 101 to which the switching element 220 contacts.

5A, the outer surface of the sealing part 112 may be recessed by a predetermined depth, or the sealing part 112 may be formed along the outer circumferential surface of the switching device 220 as shown in FIG. 5B. Like protrusions 112c having a predetermined height may be formed on the outer surface of the protrusion 112c so that the element seating grooves 112b may be formed inside the protrusions 112c.

Accordingly, when the switching elements 220 are brought close to or in contact with the sealing portion 112 of the compressor casing 101, it is possible to prevent the switching element 220 from being distorted by the compressor vibration.

6 is a cross-sectional view taken along line VI-VI in Fig. 6, and Figs. 8A and 8B are enlarged cross-sectional views of the portion "A" , Embodiments of a compressor casing and a stator support.

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 is formed with a side surface of the compression mechanism 105 and the inner space of the rear housing 120 is formed with the other side surface of the compression mechanism 105, The discharge chamber S2 is formed.

Here, a suction chamber S3 is formed on the outer side of the discharge chamber S2, one end of which communicates with the discharge chamber S2 and the other end communicates with the suction space S1. The discharge chamber S2 is communicated with the suction chamber S3 through the first oil passage F1 and the suction chamber S3 is communicated with the suction space S1 through the second oil passage F2. This will be explained later.

3, the main housing 110 is formed in a cylindrical shape with a cylindrical portion 111, a front end of the cylindrical portion 111 is integrally extended to form a closed portion 112 to be closed, An opening 113 is formed at the rear end of the housing 111. Thus, the inverter module 200 is coupled to the outer surface of the sealing portion 112, and the compression mechanism 105 is coupled to the opening 113 to seal the suction space S1. The front end of the sealing portion 112 of the main housing 110 is formed with the terminal hole 112a so that the terminal pin 107a of the first sealing terminal 107 described above can be exposed to the outside.

6 and 7, the front housing inner diameter D1 and the rear housing inner diameter D2 may be the same in the main housing 110. However, It is preferable that the rear end inner diameter D2 which is the open side is formed to be larger than the front end inner diameter D1 which is the closed side in consideration of drawing.

That is, since the main housing 110 has a rear end opened and a front end closed as described above, the mold core must be inserted so that the inner space is formed when the main housing 110 is manufactured. However, since the mold core needs to be drawn out in the opening direction when the mold is separated, the inner circumference of the inner circumferential surface of the main housing 110 may be easily drawn out from the mold core. Accordingly, it is preferable that the rear housing inner diameter D2 forming the opening of the main housing 110 is formed to be larger than the front housing inner diameter D1 constituting the closed portion.

The inner surface of the main housing 110 may be formed in a smooth tube shape. The inner surface of the main housing 110 may have a stator seat mounting portion 114 to stably fix the stator 131 of the driving motor 103, .

That is, as shown in FIGS. 8A and 8B, the inner diameter of the cylindrical portion of the main housing 110 is formed into a shape having an inner gradient? 1 with a predetermined diameter difference from the rear end to the front end. However, when the stator 131 having the same outer diameter is inserted into the main housing 110 having the inner gradient? 1, the outer diameter D3 of the stator 131 is formed to be the same in the axial direction. 110 and the outer circumferential surface of the stator 131, as shown in Fig.

A plurality of stator seating projections 114 are formed at regular intervals along the circumferential direction on the inner circumferential surface of the cylindrical portion 111 of the main housing 110 and the inner circumferential surfaces of the plurality of stator seating projections 114 are connected The inner diameter D4 of the seating projection portion may be formed to be the same from the front end to the rear end of the stator seating projection 114. [ Accordingly, even when the inner gradient? 1 is formed on the inner peripheral surface of the cylindrical portion 111 of the main housing 110 when the stator 131 having the same outer diameter is inserted into the main housing 110, the stator 131 has the same inner diameter A gap is not generated between the outer circumferential surface of the stator 131 and the inner circumferential surface of the stator seating projection 114 so that the stator 131 can be stably supported.

 Each of the stator seating projections 114 is formed in a substantially rectangular parallelepiped shape having a predetermined length in the axial direction and having a predetermined height in the radial direction. The stator mounting end 114a for supporting the front end in the axial direction can be formed stepwise. As a result, the stator 131 is prevented from moving in the axial direction, and the stator 131 can be more firmly fixed.

Here, the thickness of the main housing 110, that is, the thickness between the stator seating projections 114 may be substantially the same or may be formed differently along the longitudinal direction.

For example, the thickness of the main housing 110 between the portions where the stator seat projections 114 are formed is set such that the rear side thickness t2 is larger than the thickness of the front side Can be formed thicker than the thickness t1. However, in this case, the hardening time of the thick front side is longer than that of the thin rear side, so that a hardness difference may occur between the front end and the rear end of the main housing. Therefore, when the stator 131 is press-fitted, the stator 131 may not be firmly fixed with a difference in strain rate between both ends.

8A, when the thickness from the front side to the rear side of the main housing 110, for example, at least within the axial range of the stator seat receiving portion 114, It is preferable that the front side thickness t1 and the rear side thickness t2 are made equal to each other or at least the difference between both thicknesses is less than 15%.

For this, in the present embodiment, the inner circumferential surface of the main housing 110 is formed to have an inner slope? 1 as described above, while the outer circumferential surface of the main housing 110 is formed to have the same outer slope? 2 as the inner circumferential surface . The internal gradient? 1 and the external gradient? 2 may be the same as described above, or at least the difference between the two side slopes may be less than 15%.

Thus, in this embodiment, the hardening time between the front end and the rear end of the main housing 110 is substantially the same, and a hardness difference can be prevented from occurring between the front end and the rear end of the main housing 110, The stator 131 can be stably and firmly fixed while the stator 131 is inserted into the stator 131 in the axial direction.

However, as described above, since the inner circumferential surface of the main housing 110 has the inner gradient? 1, the thickness of the main housing 110 may be different in the portion where the stator seating projections 114 are formed . That is, the thickness t4 of the stator seat mounting portion 114 at its rear end is thicker than the thickness t3 at the front end, and the thickness of the main housing 110 is also set to the rear side of the stator seat mounting portion 114 The thickness t6 may be formed to be larger than the front side thickness t5.

8B, a uniform thickness groove 115 having a predetermined depth and width is formed on the outer circumferential surface of the main housing 110 at the portion where the stator seat receiving portion 114 is formed, so that the stator seat receiving portion 114 is formed It is possible to prevent the thickness of the main housing 110 from becoming thick. In this case, the uniform thickness groove 115 can be formed in a shape corresponding to the shape of the inner circumferential surface of the stator seat receiving portion 114, that is, the depth on the rear side is deeper than the depth on the front side. Accordingly, the thickness of the main housing 110 can be uniformly maintained, and it is possible to prevent the degree of hardening of the main housing 110 from varying due to the difference in thickness of the main housing 110 at the portion where the stator seating projections 114 are formed have.

A bearing support portion 116 is formed at the center of the inner side surface of the sealing portion 11 of the main housing 110 to receive and support a sub bearing 172 described later. The bearing support portion 116 is formed in a cylindrical shape and is protruded by a predetermined height in a direction toward the drive motor 103. This will be described again while explaining the rotating shaft.

The rear housing may further include a structure for separating the oil from the refrigerant discharged from the compression mechanism and guiding the separated oil to the compression chamber. FIGS. 9 to 13 are views showing the assembled state of the rear housing and the first scroll, and the rear face of the rear housing and the rear face of the first scroll, respectively.

9 to 11, the rear housing 120, which is the opening 113 of the main housing 110, can be coupled to the rear end of the main housing 110 via the compression mechanism 105 as described above.

The rear housing 120 includes a disc portion 121 having an exhaust port 121a and an annular portion 122 protruding from a front edge of the disc portion 121 and coupled to the main housing 110.

A housing-side discharge chamber S21 is formed in a part of the discharge chamber S2 at the central portion of the front face of the disk portion 121. [ The scroll-side discharge chamber S22 is formed on the opposite side of the housing-side discharge chamber S21, that is, on the rear side of the long plate portion 151 of the first scroll 150 to be described later. Thus, the housing-side discharge chamber S21 and the scroll-side discharge chamber S21 are combined to form the discharge chamber S2.

10, the housing-side discharge chamber S21 is formed to have an irregular shape on the inner surface 121b of the rear housing 120 and has a predetermined depth, and the housing-side discharge chamber S21 and the scroll- The discharge chambers S22 are formed in the same shape so as to be symmetrical to each other.

A first chamber separating surface 121c having a predetermined width is formed on the outer side of the housing-side discharging chamber S2, and on the outside of the first chamber separating surface 121c, A side suction chamber S31 is formed. The housing side suction chamber S31 is formed in an arc sectional shape, and the housing side suction chamber S31 and the scroll side suction chamber S32 are formed in the same shape so as to be symmetrical to each other.

The scroll side suction chamber S32 is formed on the opposite side of the housing side suction chamber S31, that is, the back side of the first hard plate portion 151, which will be described later. Thereby, the housing-side suction chamber S31 and the scroll-side suction chamber S32 are combined to form the suction chamber S3.

9 and 10, the discharge chamber S2 communicates with the suction chamber S3, and the suction chamber S3 can communicate with the suction space S1, or more precisely, with the suction chamber. For example, an oil communication hole 151d communicating between the discharge chamber S2 and the suction chamber S3 is formed at the lowermost end of the discharge chamber S2, and the suction chamber S3 is communicated with the suction chamber S1 An oil return hole 151f constituting an oil supply passage can be formed. The oil separated from the refrigerant discharged to the discharge space S3 is moved to the suction chamber S3 through the oil communication hole 151d and the oil which moves to the suction chamber S3 flows into the oil recovery hole 151f To the suction space S1 and supplied to the compression chamber. The oil communication hole and the oil recovery hole will be described again while explaining the first scroll.

On the other hand, a certain amount of oil is mixed in the refrigerant discharged from the compression mechanism unit 105 to the discharge chamber S2. Therefore, unless oil is separated from the refrigerant in the discharge chamber S2, a large amount of oil flows out of the compressor, and oil shortage may occur in the compressor.

 In view of this, conventionally, a centrifugal oil separator (not shown) is separately provided around the exhaust port to separate the oil from the refrigerant discharged from the compression mechanism. However, such a centrifugal oil separator is not limited to the above- The effective oil separation effect is inevitably low.

10, in the present embodiment, the centrifugal oil separator is excluded so that the oil collides with the wall surface of the discharge chamber S2 in the large discharge chamber S2 so as to be separated, A first oil separator 125 may be formed in the discharge chamber S2.

The first oil separating part 125 separates the oil from the refrigerant discharged from the compression mechanism part 105 so that the first oil separating part 125 is located at a position where the rear side of the compression mechanism part 105 faces Is preferably formed on the inner wall surface 121b of the housing-side discharge chamber S21.

As shown in FIG. 11, the first oil separator 125 may include an oil separation surface 125a that protrudes by a predetermined height in a direction toward the compression mechanism unit 105. The oil separation surface 125a may be formed in an elliptical cross-sectional shape or a sloped cross-sectional shape such that its peak O is located at the opposite side of the paper surface from the center.

The first oil separator 125 is formed to be positioned between the discharge port 155 formed in the first scroll 150 and the discharge port 121a formed in the rear housing 120, . That is, the outlet of the discharge port 155 and the inlet of the discharge port 121a are formed at different heights in the vertical direction, and at least a part of the first oil separation portion 125 is formed at a middle height between the discharge port 155 and the discharge port 121a As shown in FIG.

The inlet end height H1 of the exhaust port 121a from the inner side surface 121b of the housing side discharge chamber S21 is directed toward the back surface of the first scroll by at least the height H2 of the first oil- Or may protrude toward the rear surface of the first scroll 150 higher than the first oil splash surface 125a.

The first oil separator 125 is preferably formed to overlap at least a part of the exhaust port 121a formed at the center of the housing-side discharge chamber S21. Since the refrigerant discharged from the compression mechanism moves toward the discharge port 121a, the first oil separation surface 125a is located near the discharge port 121a, that is, the first oil separation portion 125 is connected to the discharge port 121a It is possible to increase the oil separation effect.

The first oil separator 125 is formed to connect the inner circumferential surfaces 121d of the rear housing 120 forming the housing-side discharge chamber S21 in the direction crossing the paper surface. It is preferable that the refrigerant discharged through the first oil separator 125 passes through the discharge port 121a, thereby increasing the oil separation effect.

The first oil separating part 125 may be formed with a second oil separating part 126 which is at least partially overlapped with the first oil separating part 125. However, the second oil separator 126 may be spaced apart from the first oil separator 125. When the second oil separating portion 126 is separated from the first oil separating portion 125, the refrigerant passes through the oil separating portion twice, thereby improving the oil separating effect.

Since the first oil separating portion 125 is formed around the exhaust port 121a in consideration of the flow direction of the refrigerant, the second oil separating portion 126 may be divided into the first oil separating portion 126, It may be difficult to place it far away from the base 125. Accordingly, it is preferable that the second oil separator 126 is formed at a position where the second oil separator 126 is partially overlapped with the first oil separator 125, and the remaining portions are spaced apart from each other.

In this case, as shown in FIG. 12A, the second oil separator 126 may be formed of a plurality of rectangular projections, or may be formed of a plurality of rectangular grooves as shown in FIG. 12B.

In consideration of the direction in which the second oil separator 126 intersects the first oil separator 125, that is, the first oil separator 125 is formed in the lateral direction, (126) may be formed in the longitudinal direction. Accordingly, the second oil-splitting surface 126a is formed in the transverse direction.

Here, the main housing 110 and the rear housing 120 may be combined to have one sealing surface. The rear surface of the main housing 110 and the front surface of the rear housing 120 corresponding to the opening 113 of the main housing 110 are coupled to each other in a state in which the rear surface of the main housing 110 is opposed to the rear surface, The front surface of the heat sink 120 may be combined to form a single sealing surface. In this case, a sealing member such as an O-ring or a gasket is provided on the rear surface of the main housing 110 or the front surface of the rear housing 120 to increase the sealing force on the sealing surface.

A discharge chamber S2 and a suction chamber S3 filled with high-pressure refrigerant or oil compressed by the compression mechanism 105 are formed between the surfaces of the main housing 110 and the rear housing 120 which are in contact with each other. Accordingly, when the sealing force between the main housing 110 and the rear housing 120 is weak, high-pressure refrigerant or oil may leak to the outside of the compressor.

In this embodiment, as shown in FIG. 9, a double sealing structure may be formed so that a multi-stage sealing surface is formed between the main housing 110 and the rear housing 120.

For example, an annular portion 121 having a predetermined height toward the main housing 110 is formed on the disc portion 121 of the rear housing 120. The outer diameter D5 of the annular portion 122 is formed smaller than the opening inner diameter D6 of the main housing 110 so that the annular portion 117 can be inserted into the opening end of the main housing 110. [

The outer sealing surface 121d is formed between the outer circumferential surface of the annular portion 122 and the front surface of the disc portion 121 so as to be stepped and the outer sealing surface 121d is formed so that the opening end surface of the main housing 110 Face to face.

The main housing 110 and the rear housing 120 form the first chamber separation surface C1 at the outer circumferential surface of the annular portion 122 and the outer sealing surface C2 at the outer sealing surface 121d, Thereby forming a sealing structure.

The first sealing member 123 and the second sealing member 124 are provided on the first chamber separating surface C1 and the outer sealing surface C2 to enhance the sealing effect. For example, an O-ring can be applied to the first sealing member 123 in consideration of the machining tolerance, and a gasket suitable for the sealing sealing of the second sealing member 124 can be applied. Accordingly, leakage of the high-pressure refrigerant and oil discharged to the discharge chamber S2 and the suction chamber S3 into the space between the engagement surfaces of the main housing 110 and the rear housing 120 can be effectively suppressed, It is possible to effectively prevent foreign substances such as brine and dust, which are generated outside the compressor, from penetrating into the inside of the compressor.

On the other hand, the refrigerant and the oil are separated from the discharge chamber, and the refrigerant is discharged to the outside of the compressor through the exhaust port, while the oil moves to the suction space and is supplied to the compression chamber.

For example, in this embodiment, as shown in Figs. 9, 10, and 13, the discharge chamber S2 and the suction chamber S3 are communicated by the oil communication hole 151d. Accordingly, the oil separated from the refrigerant in the discharge chamber S2 is moved to the suction chamber S3 through the oil communication hole 151d and the oil communication groove 151e to be described later. Therefore, the oil communication hole 151d forms the first passage F1 of the oil passage communicating between the discharge chamber S2 and the suction chamber S3.

The oil communication hole 151d is formed at the lowermost end of the discharge chamber S2 as described above. However, the oil storage grooves 121g and 151c may be formed concavely so as to collect oil around the oil communication hole 151d. The oil storage groove 121g may be formed not only in the housing-side discharge chamber S21 but also in the scroll-side discharge chamber S22.

Accordingly, the oil separated in the discharge chamber S2 is collected in the oil storage groove 121g, and the oil moves to the suction chamber S3 through the oil communication hole 151d. Therefore, it is preferable that the oil storage groove 121g is formed in the periphery of the oil communication hole 151d because the oil circulation amount can be increased. Although not shown in the drawings, the oil storage groove may be formed on only one of the housing-side discharge chamber S21 and the scroll-side discharge chamber S22.

An oil filter 127 may be provided on the inlet side of the oil communication hole 151d to block the foreign substances in the discharge chamber S2 from flowing into the oil communication hole 151d to be described later.

Here, the oil communication hole 151d may directly communicate between the discharge chamber S2 and the suction chamber S3. However, since the oil separated in the discharge chamber S2 is in a high pressure state, the high-pressure oil is sucked into the suction chamber S3 ) May cause suction loss. 13, the oil communication groove 151e for reducing the pressure of the oil separated from the discharge chamber S2 may be formed on the rear surface of the first scroll 150 contacting the rear housing 120 have. The oil communication groove 151e constitutes the second passage F2 of the oil passage and can be formed to have a sufficiently long length for reducing the pressure. For example, the second passage F2 is formed longer than the first passage F1.

The cross-sectional area of the oil communication groove 151e may be smaller than the cross-sectional area of the oil communication hole 151d and the oil recovery hole 151f. Accordingly, even if the high-pressure oil separated in the discharge chamber S2 passes through the narrow and long oil communication groove 151e and the pressure is low and moves to the suction space S1 via the suction chamber S3, The suction loss can be greatly reduced.

Although not shown in the figure, the oil communication groove 151e may be formed between the discharge chamber S2 and the suction chamber S3. However, in this case, since the chamber separating member 158 that seals and separates the chambers between the discharge chamber S2 and the suction chamber S3 is provided, the space sufficient to form the oil communication groove 151e is sufficient I can not. Accordingly, the oil communication groove 151e may be formed on the outside of the suction chamber S3, for example, on the scroll support surface 121f for supporting the first scroll 150 to the rear side in the axial direction have.

Also, although not shown in the drawing, the discharge chamber may communicate directly with the suction space without passing through the suction chamber.

The oil communication hole 151d and the oil communication groove 151e and the oil recovery hole 151f are formed in the long plate portion 151 of the first scroll 150 as in the present embodiment, Or may be formed in the housing 120. In the drawing, the second scroll is formed on the end plate of the second scroll, and this will be described again when the second scroll is described.

3, the driving motor 103, which forms the electric motor, is press-fitted into the main housing 110. As shown in FIG. 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 stator support portion 114 provided on the inner circumferential surface of the main housing 110 and the front end of the stator 131 is fixed to the rear end of the stator support portion 114 And can be supported on the stator supporting end 114a.

The stator 131 is formed by stacking a plurality of thin annular steel plates, and a coil 131a is wound on the inner circumferential surface. The gap formed between the stator supports 114 is spaced apart from the outer circumferential surface of the stator 131 so that the refrigerant sucked through the intake port 111a flows through the suction groove 154 of the first scroll 150, So that the suction passage of the refrigerant can be formed so as to be guided to the compression chamber (P).

The rotor 132 is formed by laminating a plurality of thin annular steel plates like the stator 131, and the rotating shaft 133 is press-fitted to the inner circumferential surface. The rotating shaft 133 will be described later.

Meanwhile, in the scroll compressor according to the present embodiment, the compression mechanism may be formed such that the orbiting scroll coupled to the rotary shaft is supported by the frame and is pivotally moved relative to the non-orbiting scroll to form a compression chamber. 14 is a longitudinal sectional view for explaining a compression mechanism according to the present embodiment.

The compression mechanism 105 includes a non-orbiting scroll 150 (hereinafter, referred to as a first scroll) 150 supported by the frame 140 and a second scroll 150 provided between the frame 140 and the first scroll 150, And a revolving scroll (hereinafter, referred to as a second scroll) 160 that moves.

Here, the frame 140 is coupled to the front side opening end 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 fixed to the rear side of the frame 140, And is pivotably supported on the rear surface of the frame 140 so as to pivot between the frame 150 and the frame 140.

The second scroll 160 is eccentrically coupled to the rotary shaft 133 coupled to the rotor 132 of the drive motor 103 and rotates about the first scroll 150, And a pair of compression chambers P each consisting of a suction chamber, an intermediate pressure chamber, and a discharge chamber.

The frame 140 has a disk-like rigid plate portion (hereinafter referred to as a first rigid plate portion) 141 and is protruded from the front surface of the first rigid portion 141 to form a frame Side sidewall portions (hereinafter referred to as first sidewall portions) 142 to which the two sidewall portions 142 are coupled.

A thrust surface 143 is formed on the inner side of the first sidewall portion 142 and supported by the second scroll 160 to be axially supported. A thrust surface 143 is formed at the center of the thrust surface 143, A part of the refrigerant is filled and a back pressure space S4 for supporting the back surface of the second scroll 160 is formed. A shaft hole 145 through which the rotating shaft 133 passes is formed in the back pressure space S4 and a main bearing 171 which will be described later is installed on the top surface of the shaft hole 145.

The back pressure space S4 includes a first back pressure forming member 181 provided on the thrust surface (or sealing surface) 143 between the frame 140 and the second scroll 160 and a first back pressure forming member 181 formed on the throttle surface And the second back pressure forming member 182 provided between the outer peripheral surface of the rotary shaft 133 and the outer peripheral surface of the rotary shaft 133. [

The first back pressure forming member 181 may be formed in an annular shape having a rectangular cross section and may be inserted into the annular first back pressure forming groove 143c provided on the thrust surface 143 of the frame 140. In this case, the first back pressure forming 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 back pressure forming member 182 is formed in an annular shape having a U-shaped cross section and inserted into the annular second back pressure forming groove 143b provided around the shaft hole 145 of the frame 140 . In this case, the second back pressure forming member 182 can be opened by the force of the pressure in the back pressure space S4 and sealed between the second back pressure forming member 182 and the rotating shaft 133. [

On the other hand, the first scroll 150 is formed with a hard plate portion (hereinafter referred to as a second hard plate portion) 151 in the form of a disk, and is protruded toward the first side wall portion 142 on the front surface of the second hard plate portion 151 And a pair of compression chambers P are formed at the center of the second longitudinal plate portion 151 so as to engage with the orbiting wrap 162 to be described later. And a suction port 154 communicating with the suction space S1 is formed at an edge of the second longitudinal plate portion 151. The second longitudinal plate portion 151 is formed with a second longitudinal plate portion 151, A discharge port 155 communicating from the final compression chamber to the intermediate space S4 is formed.

9 and 13, the scroll-side discharge chamber S22 described above is formed at the rear central portion of the second hard plate portion 151, and the second scroll plate discharge chamber S22 is formed outside the scroll- The scroll side suction chamber S32 is formed with the sealing surface 151a therebetween. In the scroll-side discharge chamber S22, a discharge port 155 is formed at a substantially central portion.

The scroll-side discharge chamber S22 is formed in the same shape as the housing-side discharge chamber S21 so as to form the discharge chamber S2 together with the housing-side discharge chamber S21 described above, and the scroll- S32 are formed in the same or similar shape as the housing-side suction chamber S32 so as to form the suction chamber S3 together with the housing-side suction chamber S31 described above. The second sealing surface 151a is formed in the same or similar shape as the first sealing surface 121c and the second sealing surface 151a is formed with a sealing groove 151b Is formed.

An oil storage groove 151c is formed in the lower half of the scroll-side discharge chamber S22 so that the oil separated from the refrigerant in the discharge chamber S2 can be collected. A discharge chamber S2 A first oil passage F1 for guiding the oil separated in the suction chamber S3 to the suction chamber S3 is formed.

The first oil passage F1 includes an oil communication hole 151d penetrating from the oil storage groove 151c 121g to the second sealing face 151a of the second longitudinal plate portion 151, And an oil communication groove 151e that communicates from the outlet of the communication hole 151d to the inner peripheral surface of the suction chamber S3 on the outer side and is grooved on the second sealing surface 151a.

The oil communication groove 151d forms a hole together with the first sealing face 121c and the cross-sectional area of the oil communication groove 151e is formed to be smaller than or equal to the cross-sectional area of the oil communication hole 151d. However, considering the workability, it is preferable that the oil communication groove 151e is formed to have a smaller sectional area than the oil communication hole 151d. As a result, the oil flowing into the oil communication groove through the oil communication hole passes through the oil communication groove, so that the pressure is lowered so that the intermediate pressure is lower than the pressure in the discharge chamber. Further, it is preferable that the length of the oil communication groove is made as long as possible because the oil pressure can be further lowered. Therefore, the length of the oil communication groove may be longer than the length of the oil communication hole.

At both ends of the scroll-side suction chamber S32, an oil recovery hole 151f is formed as a second oil passage for guiding the oil introduced into the suction chamber S3 into the suction space S1, that is, the suction chamber. At least one duck recovery hole 151f may be formed if it can communicate with the suction chamber.

Although not shown in the drawings, an oil recovery hole may be formed between the discharge chamber and the suction space so that the suction chamber and the discharge chamber are not communicated with each other and communicate directly from the discharge chamber to the suction space. In this case, the pressure-reducing rod may be inserted in the middle of the oil recovery hole so that when the oil in the discharge chamber passes through the oil recovery hole, it is reduced in pressure and then moved to the suction space. This makes it unnecessary to form a separate suction chamber as compared with the above-described embodiment, so that the rear housing and the second scroll can be easily processed and the sealing member for separating the chambers does not need to be provided, thereby reducing the material cost.

On the other hand, the second scroll 160 is formed in a disk shape with a hard plate portion (hereinafter referred to as a third hard plate portion) 161, and the front surface of the third hard plate portion 161 is protruded toward the second hard plate portion 151 And a second wrap 162 is formed to be engaged with the first wrap 153.

A bearing support groove 161a through which an eccentric bearing 183 to be described later is inserted is formed at the center of the front surface of the third hard plate 161. The bearing support groove 161a is provided with the third hard plate 161 in the thickness direction A back pressure hole 161b communicating with the intermediate pressure chamber at the other end is formed. As a result, the refrigerant compressed in the compression chamber flows into the back pressure space through the back pressure hole to form a back pressure, and the oil together with the refrigerant flows into the back pressure space to lubricate the bearing supporting the rotating shaft and the back pressure forming member.

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 anti-rotation mechanism according to the present embodiment includes a plurality of anti-rotation pins 191 that are coupled to the outside of the bearing support groove 161a at regular intervals along the circumferential direction.

For example, as shown in FIG. 14, an annular groove 144 may be formed in the thrust surface 143 of the frame 140. Accordingly, an inner thrust surface 143d and an outer thrust surface 143e may be formed on the inner side and the outer side of the annular groove 144, respectively.

A plurality of pin grooves 144a are formed in the annular groove 144 along the circumferential direction of the annular groove 144 at regular intervals and a plurality of pin grooves 144a are formed in the annular groove 144, The plurality of rotation prevention pins 191 are coupled to the thrust surface 163 of the scroll 160 at regular intervals along the circumferential direction.

The plurality of rotation preventing pins 191 are formed to correspond to the rotation preventing pins 191 and the pin grooves 144a so as to be inserted into the plurality of the pin grooves 144a. Accordingly, the plurality of anti-rotation pins 191 are inserted into the respective pin grooves 144a to guide the rotation of the second scroll 160 while restricting the rotation of the second scroll 160.

Here, since the outer circumferential surface of the rotation prevention pin 191 is in sliding contact with the inner circumferential surface of the pin groove 144a, it is preferable that the rotation prevention pin 191 and the pin groove 144a are made of a wear resistant material such as spring steel. However, since the second scroll 160 and the frame 140, in which the rotation prevention pin 191 and the pin groove 144a are formed, are formed of a relatively light but soft material such as an aluminum material in consideration of the weight of the compressor, The prevention pin 191 and the pin groove 144a may be poor in wear.

The anti-rotation pin 191 is made of a material having high abrasion resistance and high rigidity such as a spring steel and fixedly coupled to the second scroll 160. The anti-rotation pin 191 may be formed of a material similar to or similar to the anti- The rotation prevention mechanism having a pin-ring structure can be formed.

Here, the lubricating rings may be individually formed and assembled. However, as described above, 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. 15 to 21 are views showing an example in which a plurality of anti-rotation rings are integrated.

As shown in these drawings, the annular plate 192 according to the present embodiment includes a plate portion 194 lying between the frame 140 and the second scroll 160, and a plate portion 194 extending in the circumferential direction of the plate portion 194 And may include a plurality of ring portions 196 formed at predetermined intervals.

The plate portion 194 is formed of a thin plate material and may be formed in the same annular shape as the annular groove 144 so as to correspond to the annular groove 144 to be described later. The plate portion 194 may be either inserted into the annular groove 144 or not inserted into the annular groove 144 and positioned at a predetermined distance from the bottom surface of the annular groove 144 have. The case where the plate is inserted into the annular groove will be described in the embodiment shown in Fig.

For example, when the plate portion 194 is spaced from the annular groove 144, the inner diameter of the plate portion 194 is smaller than the outer diameter of the inner thrust surface, and the outer diameter of the plate portion 194 is equal to the outer diameter of the outer thrust surface . The inner peripheral surface of the plate portion 194 is supported on the inner thrust surface 143a of the frame 140 while the outer peripheral surface of the plate portion is supported on the outer thrust surface 143b of the frame 140. [

In particular, a plurality of fixing protrusions 194d are formed on the outer circumferential surface of the plate portion along the circumferential direction, and the fixing protrusions 194d can be inserted between the frame 140 and the first scroll 150 and fixed. In this case, a reference hole 194e may be formed in the fixed protrusion 194d so that the frame 140 and the reference pin 147, which is coupled to the first scroll 150 and holds the assembly position, passes through.

When the rear surface 194a of the plate portion 194 is spaced apart from the bottom surface of the annular groove 144 as described above, the first surface 194a of the plate portion 194, It is possible to prevent direct contact with the bottom surface of the annular groove 144, which may be advantageous in terms of friction loss.

Here, the frame 140 may be formed such that the entire thrust surface thereof is flat without forming the annular groove 144 to be described later on the thrust surface 143 thereof. In this case, however, due to the machining error of the frame or the annular plate, both axial sides of the plate portion serve as thrust surfaces, and friction loss may increase.

On the other hand, a plurality of ring portions 196 may be formed to be inserted into the pin grooves 144a, respectively. That is, the ring portion 196 according to the present embodiment is formed integrally with the plate portion 194, and is protruded from the first surface 194a of the plate portion 194 by a predetermined height in the direction toward the pin groove 144a . At this time, it is preferable that the height of the ring portion 196 is formed to be a height enough to be inserted into the pin groove 144a. Thus, rotation of the annular plate can be suppressed even if there is no separate fixing device for the annular plate.

Here, it is preferable that the ring portion 196 is integrally formed on the plate portion 194 as described above. However, considering reliability, each of the ring portions 196 is bonded or inserted to the plate portion 194 And then assembled.

On the other hand, although the ring portion is not shown in the drawing, it may be formed by simply making a hole in the plate portion. In this case, since the plate portion can rotate on the thrust surface, it is necessary to firmly fix the plate portion using the reference pin 147 and the reference hole 194e described above.

The annular plate 192 may be formed of a material having a higher rigidity than the frame 140 or the second scroll 160. Accordingly, the annular plate 192 can be prevented from being worn by contact with the rotation prevention pin 191. [

However, since the annular plate 192 may be broken during press working, it may be formed of a relatively soft material rather than a spring steel, and then formed on the outer surface thereof. The coating surface is formed of a different material from the frame 140 as well as the second scroll 160, which is effective in reducing wear.

Of course, the coating surface may be formed over the entire annular plate 192 including the inner circumferential surface of the ring portion 196, or may be formed only on the plate portion 194 except for the ring portion 196. In the case of forming only the plate portion 194, the coating surface may be formed only on the second surface 194b which forms the lubricating surface.

On the other hand, a back pressure forming member may be separately provided while integrally forming the ring portion on the annular plate. 18 is an assembled longitudinal sectional view showing the embodiment of the present invention.

18, the annular plate 192 is formed with a sealing groove 194c annularly recessed in the second surface 194b, and the backpressure forming member 181 in the annular shape is formed in the sealing groove 194c. So that the back pressure space S4 can be formed.

As described above, when the annular plate 192 is provided with a separate back pressure forming member 181, it is not necessary to process a back pressure forming groove in the frame, so that the frame 140 can be easily processed. At the same time, the clearance between the second scroll 160 and the frame 140 can be tightly blocked by using the back pressure forming member having a relatively good sealing force, so that the refrigerant leaks through the gap between the frame 140 and the second scroll 160 Can be blocked more effectively.

On the other hand, it is also possible to integrally form the ring portion on the annular plate and form the back pressure space by using the annular plate. In this case, it is not necessary to provide a separate back pressure forming member. 19 and 20 are an exploded perspective view and an assembled longitudinal sectional view for explaining an embodiment thereof.

19 and 20, a sealing surface portion 195 may be formed on the inner circumferential surface of the annular plate 192 in a direction toward the second scroll 160. As shown in FIGS.

The sealing surface portion 195 is formed by bending the second scroll 160 toward the inner circumferential surface of the plate portion 194 in a " Accordingly, the rear surface of the sealing surface portion 195 forms a sealing surface 195a contacting the thrust surface 163 of the second scroll 160.

The lower surface of the sealing surface portion 195 or the opposite surface of the sealing surface 195a is spaced apart from the thrust surface 143 of the frame 140 so that the refrigerant in the back pressure space S4 is separated from the frame 140 and the sealing surface portion 195 ). ≪ / RTI > Accordingly, it may be preferable that the sealing surface portion 195 is closely contacted in the second scroll direction.

A plurality of oil through holes 195b may be formed in the sealing surface portion 195 so that the oil in the back pressure space S4 passes through the sealing surface portion 195 and is supplied to the sealing surface 195a.

 As described above, in the present embodiment, since the annular plate 192 constituting the rotation preventing mechanism is formed with the sealing surface portion 195 together with the ring portion 194 by press working, the frame 140 is provided with a separate back pressure forming member It is possible to form a back pressure space at the center of the frame. Thus, the frame 140 can be easily processed, the sealing member can be eliminated, and the manufacturing cost can be reduced accordingly. Further, since the sealing surface portion replaces the role of the back pressure forming member, the back pressure space can be formed more quickly than in the conventional case in which the back pressure forming member floats up to a certain height to form the back pressure space, Leakage can be reduced.

On the other hand, the annular plate may be inserted into the annular groove of the frame to be coupled. Fig. 21 is a longitudinal sectional view showing an embodiment according to this.

21, an annular groove 144 is formed in the thrust surface 143 of the frame 140 to receive a plurality of pin grooves 144a, so that the annular groove 144 is formed with an annular plate 192 The plate portion 194 can be completely inserted.

In this case, the inner diameter of the plate portion 194 may be larger than the outer diameter of the inner thrust surface 143a, and the outer diameter of the plate portion 194 may be smaller than the inner diameter of the outer thrust surface 143b. The back pressure forming groove 143 may be formed in the inner thrust surface 143a so that the first back pressure forming member 181 is inserted.

However, in this case, it is preferable that the thickness of the plate portion 194 is formed to be smaller than the depth of the annular groove 144 from the viewpoint of reliability of the annular plate 192.

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 (P) is continuously moved toward the center side, and the volume is reduced.

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

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 heat generated in the switching switching device 220 attached to the outer surface of the main housing 110 can be rapidly dissipated by the heat exchange between the sealed portion 113 and the cool suction refrigerant. Further, a part of the refrigerant sucked into the suction space S1 through the intake port 111a moves toward the second bearing, which is the end of the rotary shaft, to lubricate the second bearing. Thereafter, the refrigerant passes through the stator 131 and is cooled by the driving motor 103, and then sucked into the compression chamber P.

The refrigerant sucked into the compression chamber P is compressed toward the center side along the movement path of the compression chamber P and is compressed between the first scroll 150 and the rear housing 120 through the discharge port 155 To the discharge chamber S2.

The refrigerant discharged to the discharge chamber S2 is circulated in the discharge chamber S2 to separate the refrigerant and the oil. The refrigerant is discharged to the outside of the compressor casing 101 through the discharge port 121a, The oil moves to the suction chamber S3 through the one oil passage F1 and the oil that has moved to the suction chamber S3 is moved to the suction space (or the suction chamber) S1 through the both oil return holes 151f And is supplied to the compression chamber (P) together with the refrigerant being sucked.

The refrigerant sucked into the compression chamber P is compressed while moving toward the center side along the movement path of the compression chamber P and the refrigerant compressed in the compression chamber P is discharged through the discharge port 155 to the first scroll 150 to the discharge chamber S2 formed between the rear housing 120 and the discharge chamber S2.

A part of the refrigerant compressed in the compression chamber P moves to the back pressure space S4 through the back pressure hole 161b and the refrigerant flowing into the back pressure space S4 flows through the discharge passage F3 To the front end of the rotary shaft 133, moves to the suction space S1, and is re-supplied to the compression chamber P together with the suctioned refrigerant.

At this time, the refrigerant flowing into the back pressure space S4 includes oil, and the oil moves together with the refrigerant to the suction space S1 via the rotating shaft 133, so that the main bearing 171 and the sub bearing 172, The lubricating surfaces of the first back pressure forming member 181 and the second back pressure forming member 182 are lubricated. This is possible as the discharge hole is formed in the rotary shaft 133 of the present embodiment.

That is, when the discharge hole is not formed in the rotary shaft as in the conventional art, the refrigerant and the oil flowing into the back pressure space form a kind of stagnation pressure, and the circulation of the refrigerant and the oil does not proceed smoothly.

As a result, the refrigerant and oil flowing into the back pressure space become stagnant in the back pressure space, so that the pressure of the back pressure space becomes higher or at least equal to that of the intermediate pressure chamber, so that circulation of the refrigerant from the intermediate pressure chamber to the back pressure space does not occur. Accordingly, oil can not be smoothly supplied to the lubricating surface of the bearing or the sealing member provided in the back pressure space, and friction loss is increased and wear is generated, so that the service life of the bearing and the sealing member can be shortened. In addition, the performance of the compressor may deteriorate as well as the reliability of the compressor.

In this embodiment, as the discharge passage is formed in the rotary shaft, the refrigerant in the back pressure space moves to the front end or the middle of the rotary shaft through the discharge passage, and then is discharged to the suction space of the compressor casing. Thus, the refrigerant in the intermediate pressure chamber and the oil can be continuously supplied toward the back pressure space while the inside of the back pressure space forms a kind of flow pressure. FIGS. 22 to 29 are views for explaining the rotation shaft structure for this purpose.

22 to 24B, the rotating shaft 133 according to the present embodiment is coupled to the center of the rotor 132, and an eccentric pin 136 is coupled to the rear end of the rotating shaft 133 in such a manner as to be eccentric with respect to the shaft center of the rotating shaft 133 do. The eccentric pin 136 may be inserted into the eccentric bearing 173 coupled to the bearing support groove 161a of the second scroll 160 to transmit the rotational force to the second scroll 160.

The rotary shaft 133 is formed with a discharge hole 137 in the axial direction from the rear end toward the front end and a pin hole 138 in the axial direction toward the rear end at the front end of the rotary shaft 133. The discharge hole 137 is formed along the shaft center of the rotating shaft 133 and the pin hole 138 is formed eccentrically with respect to the shaft center of the rotating shaft portion 133. Thereby, the discharge hole 137 and the pin hole 138 communicate with each other to form a discharge passage F3 that communicates the back pressure space S4 to the suction space S1.

As described above, the eccentric pin 136 is inserted and coupled to the pin hole 138, and the balance weight 134 is inserted into the eccentric pin 136 to be coupled. At this time, in a state where the eccentric pin 136 is inserted into the pin hole 138, the communication hole 138 is formed between the pin hole 138 and the discharge hole 137 so that the pin hole 138 is communicated with the discharge hole 137 A flow path 139 is formed.

The communication passage 139 has a first communication passage 139a formed along the axial direction between the inner circumferential surface of the pin hole 138 and the outer circumferential surface of the eccentric pin 136 and a second communication passage 139b formed between the first communication passage 139a and the discharge hole 137 And a second communication passage 139b communicating between the first communication passage 139 and the second communication passage 139 in the radial direction.

24A, the first communication passage 139a is formed with a cut surface 136a along the longitudinal direction on the outer circumferential surface of the eccentric pin 136, and the cut surface 136a and the inner circumferential surface of the pin hole 138 As shown in FIG.

The outer peripheral surface of the eccentric pin 136 facing the inner peripheral surface of the pin hole 138 is formed in a non-circular shape, for example, a D-cut shape, Sectional shape or an angled cross-sectional shape. However, the eccentric pin 136 may have a substantially circular cross-section, and the inner circumferential surface of the pin hole 138 facing the outer circumferential surface of the eccentric pin 136 may have a non-circular cross-sectional shape.

24B, the first communication passage 139a is formed so that at least two or more circular pin holes 138 are partially overlapped with each other, and one of the pin holes 138 has an eccentric pin 136 having a circular cross section, May be inserted and formed. That is, a remaining portion of the two or more pin holes 138, except for the portion where the pin hole 138 and the plurality of pin holes 138 are overlapped with each other, is formed in the first communication passage 139a Respectively.

The cross sectional area of the first communication passage 139a or the second communication passage 139b is smaller than the sectional area of the discharge hole 137 so that the refrigerant and oil in the back pressure space S4 are discharged through the discharge hole 137, It may be desirable to inhibit the outflow of the water.

That is, when the sectional area of the first communication passage 139a or the second communication passage 139b is larger than the sectional area of the discharge hole 137, the refrigerant flowing into the back pressure space S4 excessively flows toward the discharge hole 137 The back pressure of the back pressure space S4 may not be sufficiently formed. In addition, the pressure of the refrigerant flowing out into the suction space S1 may cause a suction loss of the compressor while forming a pressure higher than the suction pressure. Therefore, the cross-sectional area of the first communication passage 139a or the second communication passage 139b is preferably at least smaller than the cross-sectional area of the discharge hole 137. [

A communication passage 139a (139a) smaller than the sectional area of the discharge hole 137 is formed between the inner peripheral surface of the pin hole 138 and the outer peripheral surface of the eccentric pin 136 facing the inner peripheral surface of the pin hole 138, The refrigerant in the back pressure space S4 escapes toward the discharge hole 137 via the discharge passage 139b. Then, as described above, as the pressure in the back pressure space S4 is lowered to an appropriate pressure, the refrigerant in the intermediate pressure chamber moves to the back pressure space S4 together with the oil, and the first and second back pressure It is possible to effectively lubricate the forming members 181 and 182 and the bearings 171 and 173 located in the back pressure space S4.

Although not shown in the drawing, the discharge hole 137 and the pin hole 138 are spaced apart in the radial direction, and a space between the separated discharge hole 137 and the pin hole 138 is formed as a separate connection hole (not shown) You can also connect. However, this not only increases the number of processes for forming a separate connecting hole, but also the position of the pin hole may be formed too close to the outer circumferential surface of the rotary shaft, so that it may not be stably supported on the eccentric pin.

In consideration of this, it is preferable that the discharge hole 137 and the pin hole 138 are formed so as to overlap with each other in the radial direction and communicate with each other without a separate connection hole, as in the present embodiment.

For example, as shown in FIG. 25, the rear end of the discharge hole 137 and the front end of the pin hole 138 are formed with a first overlapping section L1, which is overlapped in the axial direction, and a second overlapping section And a section L2 is formed. That is, the rear end of the discharge hole 137 is located in the middle of the fin hole 138, so that the discharge hole 137 and the pin hole 138 are communicated with each other.

To this end, a rear end of the discharge hole 137 is formed with a first wedge end 137a, and a front end of the pin hole 138 is formed with a second wedge end 138a facing the front side.

A part of the first wedge stage 137a overlaps with the pin hole 138 forming the second overlapping section L2 and a part of the second wedge stage 138a overlaps with the discharge hole 137). A communication section L3 communicating in the radial direction is formed between the discharge hole 137 and the pin hole 138 so as to form the second communication passage 139b.

The communicating section L3 is a state in which the eccentric pin 136 is not inserted into the pin hole 138 or an artificial gap such as D-cut is formed between the pin hole 138 and the eccentric pin 136 It is a section that always communicates in a state of being equipped. However, when the eccentric pin 136 is circular or rotates in the pin hole 138 and the eccentric pin 136 is brought into close contact with the center of the discharge hole 137, the discharge hole 137 and the pin hole 138 The minimum communicating section L4 is formed as the communication section L3 is narrowed. This is because the insertion depth of the eccentric pin 136 is limited by the second wedge end 138a so that the minimum communication section L4 can be formed.

However, as shown in FIG. 26, a pin seating surface 139c may be formed on the inner circumferential surface of the pin hole 138 so that one end of the eccentric pin 136 is placed to limit the depth of insertion. Of course, since the eccentric pin 136 can be rotatably engaged with the pin hole 138, the pin seating surface 139c may not necessarily be formed if only the minimum communicating section L4 can be secured. However, if it is necessary to arbitrarily adjust the minimum communication hole L4 according to need, a separate pin seating surface 139c may be formed.

22, a bearing support portion 116 is formed in the main housing 110 such that a sub bearing 172 is inserted into an inner side surface of the sealing portion 112. A bearing support portion 116 is formed in the bearing support portion 116, The discharge space S5 communicating with the discharge hole 137 of the discharge port 133 is formed.

The discharge space S5 is formed to be wider than the cross sectional area of the discharge hole 137 so that the refrigerant moving through the discharge hole 137 and the oil quickly move to the discharge space S5. The oil which has moved to the discharge space S5 is lubricated with the refrigerant while moving to the suction space S1 through the clearance of the sub bearing 172 made of ball bearings and lubricating the sub bearing 172. [

Here, a bearing support surface 116a for axially supporting the sub-bearing 172 may be formed on the inner circumferential surface of the bearing support portion 116 forming the discharge space S5. The height of the bearing support surface 116a is preferably such that the bearing support surface 116a does not obstruct a clearance between the balls of the sub bearing 172. [

27, the discharge port 116b may be further formed in the middle of the bearing support portion 116 so as to communicate with the suction space S1 in the discharge space S5.

For example, when a large amount of oil is moved into the discharge space S5, the discharge hole 137 as well as the discharge space S5 are sealed with oil so that the refrigerant and the oil on the side of the back pressure space S4 smoothly flow toward the discharge space S5. You may not be able to move.

In view of this, when a discharge flow hole 116b is formed to penetrate from the inner circumferential surface to the outer circumferential surface of the bearing support portion 116 forming the middle space of the bearing support portion 116, that is, the discharge space S5, It is possible to prevent the oil from being excessively filled in the discharge space S5 by flowing the oil to be filled into the suction space S1.

On the other hand, the discharge hole 137 may be formed with an intermediate discharge hole 137b penetrating from the middle of the discharge hole 137 toward the outer peripheral surface of the rotary shaft 133, as shown in Fig. The discharge hole 137 can communicate with the suction space S1 at the front end of the rotating shaft 133 as well as at the middle of the rotating shaft.

In this case, unlike the above-described embodiment, as the discharge hole 137 is passed from the middle of the rotating shaft 133 toward the outer peripheral surface of the rotating shaft 135, the discharge hole 137 comes out of the back pressure space S4 through the discharge hole 137 A part of the oil can not be supplied to the sub-bearing 172. Therefore, in terms of lubrication to the sub-bearing 172, it may be advantageous that the discharge hole 137 is formed to penetrate to the front end of the rotation shaft 133.

In this case, however, the length of the discharge hole 137 is shortened as compared with the embodiment shown in Fig. 22, and the flow path resistance can also be lowered. As a result, the refrigerant in the back pressure space S4 quickly moves toward the suction space S1, and the oil can be supplied more smoothly toward the back pressure space S4.

On the other hand, although not shown in the drawing, the discharge hole may not communicate with the front end of the rotary shaft but may communicate with the middle discharge hole.

29 is a schematic view for explaining a process in which oil is circulated from the back pressure space to the suction space together with the refrigerant in the compressor according to FIG. As shown in the figure, when the discharge passage F3 is formed in the axial direction on the rotary shaft 133, the refrigerant (dotted line arrow) and oil (solid line arrow) flowing into the back pressure space S4 are discharged into the discharge passage F3, And then discharged into the suction space S1 of the compressor casing 101. The suction chamber S1 of the compressor casing 101 is connected to the discharge port of the compressor casing 101,

Accordingly, not only the refrigerant in the intermediate pressure chamber and the oil can be smoothly supplied to the back pressure space S4 while the inside of the back pressure space S4 forms a kind of flow pressure, and the oil contained in the refrigerant can be supplied to the rotary shaft The first back pressure forming member 181 and the second back pressure forming member 181 are moved to the suction space S1 via the discharge passage F3 of the first back pressure forming member 133 and the main bearing 171, the sub bearing 172, the eccentric bearing 173, The lubricating surface of the compressor 182 and the like can be lubricated to improve the performance and reliability of the compressor.

Claims (13)

First scroll;
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;
And a plurality of rotation preventing pins provided on the side opposite to the first scroll with the second scroll interposed therebetween and in contact with the second scroll, A frame formed along the frame; And
A plurality of ring portions extending in a circumferential direction and protruding in a direction toward a surface provided with the pin groove are formed in the plate portion, and the plurality of ring portions are formed in an annular shape Plate,
Wherein the annular plate has a sealing surface portion formed on the opposite surface of the surface on which the ring portion is formed,
And the sealing surface portion is formed to protrude annularly toward a surface provided with the rotation prevention pin. delete The method according to claim 1,
And at least one oil through hole is formed in the sealing surface portion. The method according to claim 1,
Wherein the annular plate is formed with annular recessed sealing grooves on the opposite surface of the surface on which the ring portion is formed,
And an annular sealing member is inserted into the sealing groove. The method according to claim 1,
An annular groove is formed in the frame,
And the annular plate is inserted and coupled to the annular groove. 6. The method of claim 5,
Wherein the depth of the annular groove is greater than or equal to the thickness of the annular plate. The method according to claim 1,
Wherein a fixing protrusion extending to a contact surface between the first scroll and the frame is formed on an outer circumferential surface of the annular plate,
And a reference hole is formed in the fixed protrusion such that a reference pin penetrating between the first scroll and the frame passes through the reference hole. The method according to claim 1,
And the annular plate is formed of a material different from that of the second scroll or the frame. 9. The method of claim 8,
Wherein the annular plate is formed of a material having a higher rigidity than the second scroll or the frame. The method according to claim 1,
Wherein the annular plate has a surface coated with a material different from the material of the second scroll or the frame. 11. The method of claim 10,
Wherein the coating surface is formed of a material having a higher rigidity than the second scroll or the frame. First scroll;
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;
And a plurality of rotation preventing pins provided on the side opposite to the first scroll with the second scroll interposed therebetween and in contact with the second scroll, A frame formed along the frame; And
A plurality of ring portions extending in the circumferential direction are formed in the plate portion, and the plurality of ring portions include an annular plate corresponding to the plurality of pin grooves,
Wherein a fixing protrusion extending to a contact surface between the first scroll and the frame is formed on an outer circumferential surface of the annular plate,
And a reference hole is formed in the fixed protrusion such that a reference pin penetrating between the first scroll and the frame passes through the reference hole.
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