KR20200108706A - Motor operated compressor - Google Patents

Abstract

The present invention relates to an electric compressor. An object of the present invention is to provide a structure of a compressor in which ease of assembly of the compressor can be improved. The electric compressor according to the present invention comprises: a rotary shaft; a first scroll provided on one side of the rotary shaft; a second scroll which is engaged with the first scroll to form a compression chamber between the first scroll and the second scroll, and having a ring receiving groove formed on the surface opposite to the surface facing the first scroll; and a pin and a ring formed to rotate the second scroll relative to the first scroll, by providing the pin, at least a part of which is positioned in the ring receiving groove to guide movement of the second scroll, and the ring positioned between the pin and the ring receiving groove. The ring may be thread-coupled into the ring receiving groove.

Description

Electric compressor {MOTOR OPERATED COMPRESSOR}

The present invention relates to a compressor, and more particularly to a scroll compressor.

In general, compressors that compress a refrigerant in a vehicle air conditioning system have been developed in various forms, and in accordance with a recent trend of electrification of automobile parts, the development of electric compressors driven by electricity using a motor has been actively made.

Among several compression methods, a scroll compression method suitable for high compression ratio operation is mainly applied to the electric compressor. In such a scroll type electric compressor, a motor part made of a rotary motor is installed inside a sealed casing, and a compression part made up of a non-orbiting scroll and an orbiting scroll is installed at one side of the motor part. In addition, the motor unit and the compression unit are connected by a rotation shaft so that the rotational force of the motor unit is transmitted to the compression unit.

The rotational force transmitted to the compression unit rotates the orbiting scroll with respect to the non-orbiting scroll, so that the refrigerant is sucked into both compression chambers into a pair of compression chambers formed between the orbiting scroll and the non-orbiting scroll, and then compressed and discharged.

Such a scroll type compressor has a rotation preventing mechanism for preventing the rotating scroll from rotating. The anti-rotation mechanism may be applied with an Oldham ring or a pin and ring.

In particular, in the anti-rotation mechanism according to the pin and ring method, the rotation of the orbiting scroll is prevented as the pin installed on the member facing the orbiting scroll contacts the inner circumferential surface of the ring inserted into the groove of the orbiting scroll and slides. Will be prevented.

Such a pin and ring method is a method of inserting the ring into a groove formed on the rear surface of the orbiting scroll, and fixing the ring by press-fitting (or hot press-fitting) into the groove, and between the outer peripheral surface of the ring and the inner peripheral surface of the groove. A method has been proposed in which the ring is slidably coupled to the groove by engaging so as to leave a predetermined gap.

According to the former method, deformation of the orbiting scroll occurs in the process of pressing the ring into the groove. In particular, when deformation occurs in the orbiting wrap forming the side of the compression chamber, there may be a problem that friction increases or compression efficiency decreases compared to the designed one.

On the other hand, the latter method is disclosed in Prior Document 1 [US 2004/0067147 A (published on Apr. 08, 2004)] and Prior Document 2 [Japanese Patent Laid-Open Publication No. JP 2015-083780 A (published on Apr. 30, 2015)]. In this way, in the method of coupling so as to leave a predetermined gap between the outer circumferential surface of the ring and the inner circumferential surface of the groove, there is an advantage that deformation of the orbiting scroll by press fitting does not occur.

However, in general, when the compressor is manufactured, a problem occurs in that the ring is separated from the groove due to gravity in the assembly process in which the compressor is assembled with the slewing wrap facing the upper side and the groove into which the ring is inserted facing the ground surface.

Accordingly, there is a need to develop a pin and ring that is easy to assemble without causing deformation to the orbiting scroll.

US patent application publication publication US 2004/0067147 A (published on Apr. 08, 2004) Japanese Patent Application Publication JP 2015-083780 A (published on April 30, 2015)

It is an object of the present invention to provide a structure of a compressor capable of improving the ease of assembly of a compressor by preventing the ring from being separated from the groove when assembling the compressor without causing deformation to the orbiting scroll in the pin-and-ring type anti-rotation mechanism. It is in offering.

In addition, an object of the present invention is to provide a structure of a compressor in which a ring receiving groove formed in a rotating scroll and a ring inserted therein can be assembled by a screw fastening method in a pin-and-ring type anti-rotation mechanism. have.

In addition, an object of the present invention is to provide a structure of a compressor capable of assembling a pin-and-ring type anti-rotation mechanism in a state in which the ring is adhered to the orbiting scroll due to the viscosity of oil when assembling the compressor.

An electric compressor according to an embodiment of the present invention comprises a rotating shaft, a first scroll provided on one side of the rotating shaft, and forming a compression chamber between the first scroll by meshing with the first scroll, and facing the first scroll. A second scroll in which a ring receiving groove is formed on the opposite side of the surface, at least a portion of which is located in the ring receiving groove, and a pin configured to guide the movement of the second scroll, and a ring positioned between the pin and the ring receiving groove Thus, it includes a pin and ring formed to rotate the second scroll with respect to the first scroll, the ring may be coupled by screwing into the ring receiving groove.

Accordingly, when the compressor is assembled, the ring is not separated from the ring receiving groove, so that the compressor may be easily assembled.

Here, a screw groove may be formed on an inner peripheral surface of the ring receiving groove, and a thread corresponding to the screw groove may be formed on an outer peripheral surface of the ring. Since such threads and screw grooves can generally be formed through cutting, deformation of the orbiting scroll can be prevented.

In addition, the ring may include a first fastening groove formed by being recessed on one side of the inner circumferential surface of the ring, and a second fastening groove formed at a position facing the first fastening groove. Accordingly, the ring can be easily fastened to the ring receiving groove by inserting and rotating a tool such as a screwdriver between the first fastening groove and the second fastening groove.

In addition, in this embodiment, the first and second fastening grooves may extend in the axial direction from the inner peripheral surface of the ring.

Here, the length of the first and second fastening grooves in the axial direction may be smaller than the length of the ring in the axial direction.

In addition, in this embodiment, the first and second fastening grooves each intersect the inner circumferential surface of the ring and include first and second surfaces facing each other, and the first and second surfaces are respectively It can be connected round. Accordingly, it is possible to prevent the pin from hitting the edges of the first and second fastening grooves and causing damage.

In addition, according to a modified example of an embodiment of the present invention, the ring may include a side wall on an outer circumferential surface on which the thread is formed, an inner wall crossing the side wall and including an inner surface facing the end surface of the pin. Here, the inner wall may include a fastening groove formed by being recessed in the inner surface and extending along a direction on the inner surface.

Here, the end surface of the pin may be spaced apart from the inner surface. Accordingly, damage due to the pin being rubbed against the fastening groove can be prevented.

In addition, the electric compressor according to the present invention further comprises a main frame provided on the opposite side of the first scroll with the second scroll interposed therebetween, and supporting the second scroll in an axial direction, wherein the pin 2 It may be installed on one surface of the main frame facing the scroll.

An electric compressor according to another embodiment of the present invention includes a rotating shaft, a first scroll provided on one side of the rotating shaft, and forming a compression chamber between the first scroll by engaging the first scroll, and facing the first scroll. A second scroll in which a ring receiving groove is formed on a second surface opposite to the first surface, at least part of which is located in the ring receiving groove to guide the movement of the second scroll, and located between the pin and the ring receiving groove And a pin and ring formed to rotate the second scroll with respect to the first scroll. Here, the ring is inserted into the ring receiving groove, and includes a first portion that slides with respect to the pin and a second portion formed to cover at least a portion of the second surface, and the second portion is a first It may be formed to protrude from the portion in the axial direction.

In addition, in this embodiment, the second portion may include an oil reservoir surface formed concave on one surface facing the second scroll of the second portion to form an oil receiving portion between the second portion and the second scroll. have.

In addition, in a modified example of the present embodiment, the rotation shaft is formed to penetrate the second scroll and supported in a radial direction by the first scroll, and a through groove in which at least a part of the rotation shaft is provided is formed in the second part. I can.

According to the present invention, as the ring is coupled to the ring receiving groove by screwing, the ring can be fixed to the ring receiving groove without deformation of the orbiting scroll. Accordingly, when the compressor is assembled, the ring may be prevented from being separated from the groove, thereby improving the ease of assembly of the compressor. Due to this, the productivity of the compressor can be improved.

In addition, according to the present invention, since the ring can be easily fastened to the ring receiving groove through a tool such as a screwdriver, assembly of the compressor can be made easier.

In addition, when the compressor is assembled, the ring may be assembled in a state that is adhered to the orbiting scroll due to the viscosity of the oil, so that the ring may be prevented from being separated from the groove when assembling the compressor, thereby improving the ease of assembly of the compressor.

1 is a perspective view of an electric compressor according to the present invention.
2 is an exploded perspective view of the electric compressor shown in FIG. 1.
3 is a cross-sectional view of the electric compressor shown in FIG. 1.
4 is a view showing a coupling relationship between the orbiting scroll and the pin and ring according to the present invention.
5A is an enlarged view showing a cross section in which a pin and ring is installed according to an embodiment of the present invention.
5B is a view as viewed from above of the ring shown in FIG. 5A.
6A is a view showing a longitudinal section of a ring according to a modified example of an embodiment of the present invention.
6B is a view as viewed from above of the ring shown in FIG. 6A.
7 is a view showing another application example of the pin and ring according to an embodiment of the present invention.
8A is a view showing a state in which a pin and ring is installed according to another embodiment of the present invention.
FIG. 8B is a view showing the ring of the pin and ring shown in FIG. 8A from above.
9A is a view showing an application example of a pin and ring according to a modified example of another embodiment of the present invention.
9B is a view from above of the ring of the pin and ring shown in FIG. 9A.

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

In the present specification, the same or similar reference numerals are assigned to the same and similar configurations even in different embodiments, and the description is replaced with the first description.

When a component is referred to as being "connected" or "connected" to another component, it is understood that it may be directly connected or connected to the other component, but other components may exist in the middle. Should be. On the other hand, when a component is referred to as being "directly connected" or "directly connected" to another component, it should be understood that there is no other component in the middle.

Singular expressions used in the present specification include plural expressions unless the context clearly indicates otherwise.

1 is a perspective view showing the appearance of the electric compressor 1000 proposed in the present invention.

The electric compressor 1000 includes a compression module 1100 and an inverter module 1200.

The compression module 1100 refers to a set of components for compressing a fluid such as a refrigerant. The inverter module 1200 refers to a set of components for controlling the driving of the compression module 1100. The inverter module 1200 may be coupled to one side of the compression module 1100. If the direction is set based on the flow of the fluid compressed by the electric compressor 1000, one side of the compression module 1100 refers to the front side of the compression module 1100. Since the fluid to be compressed is introduced into the intake port 1111a and discharged through the discharge port 1121a, the inverter module 1200 disposed close to the intake port 1111a may be described as being coupled to the front side of the compression module 1100.

The outer appearance of the compression module 1100 may be formed by the main housing 1110, the main frame 1120, the middle housing 1130, and the rear housing 1140. The main housing 1110, the main frame 1120, the middle housing 1130, and the rear housing 1140 are sequentially disposed from the front side to the rear side of the electric compressor 1000.

The main housing 1110 has a hollow cylinder, a polygonal column, or an appearance equivalent thereto. The main housing 1110 may be disposed to extend in the transverse direction. The main housing 1110 is formed to surround the electric unit 1150 to be described later. Both ends of the main housing 1110 may be open. Here, the front end of the main housing 1110 refers to an end coupled to the inverter module 1200. Further, the rear end of the main housing 1110 refers to an end coupled to the main frame 1120.

A suction part 1111 is formed on the outer peripheral surface of the main housing 1110. The suction part 1111 forms a flow path for supplying the fluid to be compressed to the internal space of the compression module 1100.

The main frame 1120 is disposed on the rear side of the main housing 1110. The main frame 1120 may have an outer diameter corresponding to the outer diameter of the main housing 1110 or may have an outer diameter corresponding thereto. The main frame 1120 is configured to support the fixed scroll 1161 of the compression unit 1160 to be described later, and does not necessarily need to be exposed to the outside of the compression module 1100. However, in the present invention, since the discharge part 1121 is formed in the main frame 1120, at least a part of the main frame 1120 must be exposed to the outside of the compression module 1100.

The discharge part 1121 is formed to discharge the fluid compressed by the electric compressor 1000 to the outside. The discharge part 1121 may have a portion protruding from the outer peripheral surface of the main frame 1120. The discharge part 1121 may be connected to a discharge pipe (not shown) that supplies the fluid compressed by the electric compressor 1000 to the next device of the refrigeration cycle.

The middle housing 1130 has a hollow cylinder, a polygonal column, or an appearance equivalent thereto. The middle housing 1130 may be disposed to extend in the transverse direction. The middle housing 1130 is formed to surround the compression unit 1160. Both ends of the middle housing 1130 may be open. Here, the front end of the middle housing 1130 refers to an end coupled to the main frame 1120. In addition, the rear end of the middle housing 1130 refers to an end coupled to the rear housing 1140.

The rear housing 1140 is installed on the rear side of the middle housing 1130. The rear housing 1140 may be formed to cover the rear end of the middle housing 1130.

The main housing 1110, the main frame 1120, the middle housing 1130, and the rear housing 1140 may be coupled to each other by a plurality of fastening members 1142. The fastening member 1142 is inserted from the rear housing 1140 side toward the main housing 1110 side. A plurality of fastening members 1142 may be installed along the circumference of the rear housing 1140 to be spaced apart from each other.

The exterior of the inverter module 1200 is formed by the inverter housing 1210 and the inverter cover 1220. The inverter housing 1210 and the inverter cover 1220 are coupled to each other and form a mounting space for circuit components and the like.

Next, the internal structure of the electric compressor 1000 will be described.

2 is an exploded perspective view of the compression module 1100 shown in FIG. 1. 3 is a cross-sectional view of the electric compressor 1000 shown in FIG. 1.

The electric compressor 1000 includes a compression module 1100 and an inverter module 1200.

The compression module 1100 includes a main housing 1110, an electric unit 1150 (a driving unit or a driving motor), a compression unit 1160, a rotating shaft 1170, a bush bearing 1181, 1182, a rear housing 1140, and rotating. A prevention mechanism 1180, a rear housing 1140, a main frame 1120, various sealing members 1192, 1193, 1194, 1195, and the like are included.

Both the front and rear ends of the main housing 1110 are open ends. Here, the front end refers to the inverter module 1200 side, and the rear end refers to the main frame 1120 side. The front end may be referred to as a first end, and the rear end may be referred to as a second end. The inverter module 1200 is coupled to the front end of the main housing 1110, and the main frame 1120 is coupled to the rear end of the main housing 1110.

The main housing 1110 forms a motor chamber S1. The motor room S1 means a space in which the electric unit 1150 is installed. The main housing 1110 is formed to accommodate the electric unit 1150 in the motor chamber S1. The electric unit 1150 is seated in the motor chamber S1 of the main housing 1110. The inverter module 1200 is installed at the front end of the main housing 1110, and the main frame 1120 is installed at the rear end of the main housing 1110.

The transmission unit 1150 is formed to generate a driving force for rotating the orbiting scroll 1162 of the compression unit 1160. The electric unit 1150 is composed of a drive motor. The drive motor is installed in the motor chamber S1. The drive motor includes a stator 1151 and a rotor 1152.

The stator 1151 is installed along the inner circumferential surface of the main housing 1110. The stator 1151 is fixed to the inner circumferential surface of the main housing 1110. The stator 1151 is inserted and fixed to the main housing 1110 by shrink fit (or hot press fit).

The rotor 1152 is installed in an area surrounded by the stator 1151. When power is applied to the stator 1151 through the three-phase terminal 1153, the rotor 1152 rotates due to electromagnetic interaction with the stator 1151.

The compression unit 1160 is formed to compress a fluid to be compressed, such as a refrigerant. The compression unit 1160 is formed on the rear side of the transmission unit 1150. The compression unit 1160 includes a fixed scroll 1161 and an orbiting scroll 1162. The compression unit 1160 is formed by a fixed scroll 1161 and an orbiting scroll 1162. The fixed scroll 1161 and the orbiting scroll 1162 may be referred to as a first scroll and a second scroll, respectively.

The fixed scroll 1161 and the orbiting scroll 1162 are combined with each other to form a pair of compression chambers. As the orbiting scroll 1162 rotates, the volume of the compression chamber is repeatedly changed, and accordingly, a fluid such as a refrigerant is compressed in the compression chamber.

The fixed scroll 1161 is disposed relatively close to the electric unit 1150, and the orbiting scroll 1162 is disposed relatively far from the electric unit 1150. The fixed scroll 1161 is disposed between the orbiting scroll 1162 and the main housing 1110 in the axial direction. The orbiting scroll 1162 is disposed between the fixed scroll 1161 and the rear housing 1140 in the axial direction.

The fixed scroll 1161 is supported by the middle housing 1130 in the radial direction of the rotation shaft 1170. Further, the fixed scroll 1161 is supported by the main frame 1120 in the axial direction of the rotation shaft 1170.

The fixed scroll 1161 is disposed at a position corresponding to the bearing 1172 of the rotating shaft 1170. The rotation shaft 1170 passes through the fixed scroll 1161.

The orbiting scroll 1162 is disposed at a position facing the fixed scroll 1161. The orbiting scroll 1162 is coupled to the eccentric portion 1173 of the rotation shaft 1170. Accordingly, the orbiting scroll 1162 is eccentrically coupled to the rotation shaft 1170. The orbiting scroll 1162 receiving the rotational force through the eccentric portion 1173 is rotated by the rotation preventing mechanism 1180.

The fixed scroll 1161 includes a fixed plate part 1161a, a fixed wrap 1161b, a side wall part 1161c, a rotating shaft receiving part 1161d, a sealing member receiving part 1161e, and a fixed scroll side suction flow path 1161f1, 1161f2. , A fixed scroll side discharge passage 1161g, a fixed scroll side oil hole 1161h, and a fixed scroll side oil supply passage 1161i.

The fixed plate portion 1161a is formed in a plate shape facing the base 1121b at a position spaced apart from the base 1121b of the main frame 1120. The fixed plate portion 1161a may have a circular cross section, and in this case, the fixed plate portion 1161a has a shape of a disk.

If the side facing the main frame 1120 among both sides of the fixed plate portion 1161a is referred to as the first side, and the side facing the orbiting scroll 1162 is referred to as the second side, the first side includes a rotating shaft receiving portion 1161d. ) Is formed, and a fixing wrap 1161b is formed on the second surface.

The fixed wrap 1161b protrudes toward the orbiting scroll 1162 in an involute curve, an arithmetic spiral (Archimedean spiral), or a logarithmic spiral (Logarithmic spiral) shape. The fixing wrap 1161b may be formed in various shapes in addition to that. The fixed wrap 1161b is engaged with the orbiting wrap 1162b to form a compression chamber.

The side wall portion 1161c protrudes toward the orbiting scroll 1162 side along the rim of the fixed plate portion 1161a. The sidewall portion 1161c is formed to surround the fixed wrap 1161b in the radial direction of the fixed scroll 1161. The outer peripheral surface of the side wall portion 1161c is in close contact with the inner peripheral surface of the middle housing 1130. Accordingly, the fixed scroll 1161 may be fixed to the inner side of the middle housing 1130.

The rotation shaft receiving portion 1161d is formed in the center of the fixed plate portion 1161a. The rotating shaft receiving portion 1161d protrudes in the axial direction from the fixed plate portion 1161a toward the main housing 1110. The rotation shaft receiving portion 1161d is inserted into the main frame 1120.

The rotation shaft receiving portion 1161d is formed to surround the bearing 1172 of the rotation shaft 1170 and is formed to receive the bearing 1172. The rotation shaft receiving portion 1161d may be formed in a hollow cylindrical shape.

A sealing member accommodating portion 1161e is formed on the outer circumferential surface of the rotating shaft accommodating portion 1161d. The sealing member accommodating portion 1161e is formed by being recessed along the circumferential direction on the outer circumferential surface of the rotating shaft accommodating portion 1161d. A sealing member 1192 for sealing an oil separation chamber S4 to be described later is installed in the sealing member accommodating portion 1161e. The sealing member 1192 is formed to surround the outer circumferential surface of the rotation shaft receiving portion 1161d.

The fixed scroll side suction passages 1161f1 and 1161f2 are formed in the fixed plate portion 1161a. The fixed scroll side suction flow paths 1161f1 and 1161f2 are formed of holes penetrating the fixed plate portion 1161a in the axial direction. The fixed scroll side suction passages 1161f1 and 1161f2 are configured to supply the compression target fluid flowing into the motor chamber S1 through the suction unit 1111 to the compression unit 1160.

The fixed scroll side suction passages 1161f1 and 1161f2 are formed at positions facing the main frame side suction passages 1121c1 and 1121c2 formed in the main frame 1120 in the axial direction. Based on the radial direction of the rotating shaft 1170, the fixed scroll side suction passages 1161f1 and 1161f2 are formed outside the partition wall 1121d, which will be described later, and formed inside the sidewall portion 1161c of the fixed scroll 1161 do.

The fixed scroll side suction passages 1161f1 and 1161f2 may be formed in plural. The plurality of fixed scroll side suction passages 1161f1 and 1161f2 may be formed on opposite sides of the rotation shaft receiving portion 1161d in the radial direction of the rotation shaft 1170.

The fixed scroll side discharge passage 1161g is formed in the fixed plate portion 1161a. The fixed scroll-side discharge passage 1161g is configured to discharge the fluid compressed in the compression unit 1160 into the discharge chamber S2.

The fixed scroll side discharge passage 1161g is formed at a position corresponding to the discharge chamber S2 in the axial direction of the rotation shaft 1170. The fixed scroll side discharge passage 1161g is formed inside the partition wall 1121d to be described later based on the radial direction of the rotation shaft 1170. A discharge valve 1163 for opening and closing the fixed scroll side discharge passage 1161g is installed between the fixed scroll 1161 and the main frame 1120.

The fixed scroll side oil hole 1161h is formed in the fixed plate portion 1161a or the side wall portion 1161c. The fixed scroll side oil hole 1161h is opened toward the main frame 1120 in one side. In the radial direction of the rotation shaft 1170, the fixed scroll side oil hole 1161h is formed outside the partition wall 1121d, which will be described later, and is formed at the same position as the sidewall portion 1161c of the fixed scroll 1161 or inside it. do.

The fixed scroll side oil hole 1161h is formed to face the main frame side oil hole 1121i in the axial direction. The fixed scroll side oil hole 1161h corresponds to an inlet of the fixed scroll side oil supply passage 1161i. The fixed scroll side oil hole 1161h may be in close contact with the main frame side oil hole 1121i.

The fixed scroll side oil supply passage 1161i is formed on the downstream side of the fixed scroll side oil hole 1161h. The fixed scroll-side oil supply passage 1161i penetrates a part of the side wall portion 1161c in the axial direction, and penetrates a part of the fixed plate portion 1161a in the radial direction of the rotation shaft 1170. The outlet of the fixed scroll side oil supply passage 1161i is formed to be exposed to the inner circumferential surface of the fixed scroll 1161.

Bush bearings 1181 and 1182 and/or a rotating shaft 1170 are disposed on the inner circumferential surface of the fixed scroll 1161. Oil flowing from the oil separation chamber (S4) formed in the main frame (1120) is through the fixed scroll side oil hole (1161h) and the fixed scroll side oil supply passage (1161i) through the bush bearings (1181, 1182) and the rotation shaft. It is supplied as (1170).

The orbiting scroll 1162 includes an orbiting plate portion 1162a, a orbiting wrap 1162b, a rotating shaft receiving portion 1162c, a ring receiving groove 1162d, and an intermediate pressure discharge passage 1162e.

The turning plate portion 1162a is formed in a plate shape corresponding to the fixed plate portion 1161a. If the turning plate portion 1162a has a cross section corresponding to a circle, the turning plate portion 1162a has a shape of a disk.

The orbiting plate portion 1162a may have an outer diameter smaller than that of the sidewall portion 1161c of the fixed scroll 1161. Accordingly, the orbiting plate portion 1162a may be seated on the fixed wrap 1161b of the fixed scroll 1161. The turning hard plate portion 1162a and the fixing wrap 1161b may form a thrust surface.

When the side facing the fixed scroll 1161 of both sides of the orbiting plate portion 1162a is referred to as the first side, and the side facing the rear housing 1140 is referred to as the second side, the first side is the orbiting wrap 1162b Is formed, and a ring receiving groove 1162d is formed on the second surface.

The orbiting wrap 1162b is an involute curve, an arithmetic spiral (Archimedean spiral), or a logarithmic spiral (Logarithmic spiral) from the first side of the orbiting plate portion 1162a toward the fixed scroll 1161 It protrudes in shape. The orbiting wrap 1162b may be formed in various other shapes.

The orbiting wrap 1162b may be in close contact with the fixed plate portion 1161a. Likewise, the fixed wrap 1161b may also be in close contact with the turning hard plate 1162a. At least one of the axial end of the fixed wrap 1161b and the axial end of the orbiting wrap 1162b is provided with a tip chamber to seal the compression chamber.

The rotating shaft receiving portion 1162c is formed in the center of the turning plate portion 1162a. The rotation shaft receiving portion 1162c protrudes toward the fixed scroll 1161 from the first surface of the turning plate portion 1162a. The rotation shaft receiving portion 1162c may be formed at a position corresponding to the basic circle of the involute shape defining the orbiting wrap 1162b. Accordingly, the rotation shaft receiving portion 1162c forms the innermost part of the orbiting wrap 1162b.

The rotation shaft receiving portion 1162c is formed in a hollow cylindrical shape to accommodate the eccentric portion 1173 of the rotation shaft 1170. The rotation shaft receiving portion 1162c is formed to surround the eccentric portion 1173 of the rotation shaft 1170.

Unlike the rotating shaft receiving portion 1161d of the fixed scroll 1161 completely penetrating the fixed plate portion 1161a, the rotating shaft receiving portion 1162c of the orbiting scroll 1162 is opened only to one side. For example, the rotation shaft receiving portion 1162c of the orbiting scroll 1162 is opened toward the fixed scroll 1161, but the opposite side of the opened portion is blocked by the orbiting plate portion 1162a. Accordingly, the eccentric portion 1173 of the rotating shaft 1170 is inserted into the rotating shaft receiving portion 1162c of the orbiting scroll 1162, but does not penetrate the orbiting plate portion 1162a.

The intermediate pressure discharge passage 1162e is formed to penetrate the turning plate portion 1162a in the axial direction of the rotation shaft 1170 or in a direction inclined to the axial direction. The intermediate pressure discharge passage 1162e communicates the compression chamber and the intermediate pressure chamber S3 with each other so that the medium pressure fluid is discharged to the intermediate pressure chamber S3 formed between the orbiting scroll 1162 and the rear housing 1140. The intermediate pressure discharge passage 1162e is formed outside the fixed scroll side discharge passage 1161g in the radial direction of the rotation shaft 1170 and is formed inside the fixed scroll side suction passages 1161f1 and 1161f2. Accordingly, the pressure of the fluid discharged from the intermediate pressure discharge passage 1162e to the intermediate pressure chamber S3 is between the suction pressure and the discharge pressure of the fluid.

Next, the rotation shaft 1170 will be described.

The rotating shaft 1170 is coupled to the rotor 1152, the fixed scroll 1161, and the orbiting scroll 1162. The rotation shaft 1170 rotates together with the rotor 1152 and transmits the rotational force generated by the driving motor to the compression unit 1160. The rotating shaft 1170 is inserted and fixed to the rotor 1152 by a method of shrink fit (or hot press fit).

The rotation shaft 1170 extends from the front side to the rear side of the electric compressor 1000. The direction in which the rotation shaft 1170 extends is the axial direction of the rotation shaft 1170. The rotary shaft 1170 is connected to the electric unit 1150 and the orbiting scroll 1162 to transmit the driving force generated by the electric unit 1150 to the orbiting scroll 1162, respectively.

The rotation shaft 1170 includes a drive motor coupling portion 1171, a bearing 1172, and an eccentric portion 1173.

The drive motor coupling portion 1171 is coupled to the rotor 1152. The drive motor coupling portion 1171 extends along the axial direction of the rotation shaft 1170 and passes through the center of the rotor 1152.

The bearing 1172 is a part corresponding to the rear side of the drive motor coupling part 1171. The bearing 1172 extends along the axial direction from the drive motor coupling portion 1171. The bearing 1172 may have an outer diameter different from that of the driving motor coupling portion 1171. The center of the bearing 1172 coincides with the center of the drive motor coupling portion 1171.

The bearing 1172 is inserted into the rotation shaft receiving portion 1161d of the fixed scroll 1161 to be described later. The bearing 1172 passes through the rotation shaft receiving portion 1161d. The circumference of the bearing 1172 is rotatably supported by the rotation shaft receiving portion 1161d in the radial direction of the rotation shaft 1170.

The eccentric part 1173 is a part corresponding to the rear side of the bearing 1172. The eccentric portion 1173 extends along the axial direction from the bearing 1172. The eccentric portion 1173 may have an outer diameter smaller than that of the bearing 1172.

The center of the eccentric part 1173 does not coincide with the center of the bearing 1172. Accordingly, the center of the eccentric portion 1173 is formed at a position eccentric from the center of the drive motor coupling portion 1171 or the center of the bearing 1172 in the axial direction of the rotation shaft 1170. The eccentric portion 1173 is formed at the rear end of the rotation shaft 1170. The eccentric portion 1173 is inserted into the rotation shaft receiving portion 1161d of the orbiting scroll 1162 to be described later.

The front end 1174 of the rotation shaft 1170 is supported by a rotation shaft support part 1121 formed in the inverter module 1200. The rotation shaft support 1121 protrudes from the inverter cover 1220 or the inverter housing 1210 toward the motor chamber S1. The rotation shaft support part 1121 is formed to support the front end 1174 of the rotation shaft 1170 so as to be rotatable in the axial direction.

The front end 1174 of the rotation shaft 1170 may have a smaller outer diameter than the driving motor coupling portion 1171. A bearing 1196 may be installed between the front end 1174 of the rotation shaft 1170 and the support portion of the rotation shaft 1170. The bearing 1196 may be formed to surround the rotation shaft 1170. The bearing 1196 may be configured as a ball bearing.

The rotation shaft 1170 is formed with an oil supply passage 1175 and an oil supply hole 1176 on the rotation axis side. The rotation shaft side oil supply passage 1175 is formed by being recessed along the axial direction of the rotation shaft 1170 at the rear end of the rotation shaft 1170. In addition, the oil supply hole 1176 is formed toward the radial direction of the rotation shaft 1170 in the oil supply passage 1175 on the rotation shaft side. The oil supply hole 1176 may be formed in plural, and the plurality of oil supply holes 1176 are formed at positions spaced apart from each other in the axial direction of the rotation shaft 1170.

The first oil supply hole 1176a is disposed to face the oil supply hole 1181a formed in the first bush bearing 1181. The first oil supply hole 1176a receives oil from the fixed scroll side oil supply passage 1161i through the oil supply hole 1181a of the first bush bearing 1181. Oil supplied to the first oil supply hole 1176a is supplied to the second oil supply hole 1176b and the third oil supply hole 1176c through the oil supply passage 1175 on the rotating shaft side.

The second oil supply hole 1176b is disposed to face the inner circumferential surface of the first bush bearing 1181. In addition, the third oil supply hole 1176c is disposed to face the inner circumferential surface of the second bush bearing 1182. Oil supplied to the rotary shaft side oil supply passage 1175 is supplied between the outer peripheral surface of the rotary shaft 1170 and the inner peripheral surfaces of the two bush bearings 1181 and 1182 through the second oil supply hole 1176b and the third oil supply hole 1176c. Oil supplied to the second oil supply hole 1176b and the third oil supply hole 1176c lubricates the rotating shaft 1170 and the bearing surface between the two bearings 1181 and 1182.

The first bush bearing 1181 is inserted into the rotating shaft receiving portion 1161d of the fixed scroll 1161. The outer peripheral surface of the first bush bearing 1181 is in close contact with the inner peripheral surface of the rotation shaft receiving portion 1161d. The first bush bearing 1181 is fixed to the rotation shaft receiving part 1161d.

The first bush bearing 1181 is formed in a hollow cylindrical shape so as to surround the bearing 1172 of the rotation shaft 1170. The bearing 1172 is inserted into the first bush bearing 1181. The rotation shaft 1170 rotates relative to the first bush bearing 1181. The inner circumferential surface of the first bush bearing 1181 and the outer circumferential surface of the bearing 1172 form a bearing surface.

An oil supply hole 1181a is formed in the first bush bearing 1181. The oil supply hole 1181a of the first bush bearing 1181 is opened toward the radial direction of the rotation shaft 1170. The oil supply hole 1181a on the outer circumferential surface of the first bush bearing 1181 is disposed so as to face the fixed scroll side oil supply passage 1161i formed in the fixed scroll 1161, and is disposed on the inner circumferential surface of the first bush bearing 1181. The oil supply hole 1181a is disposed to face the first oil supply hole 1176a of the rotation shaft 1170.

Accordingly, the oil supplied from the fixed scroll side oil supply passage 1161i passes through the oil supply hole 1181a of the first bush bearing 1181 and the first oil supply hole 1176a of the rotation shaft 1170 to the rotation shaft side oil supply passage 1175. Is supplied as

The second bush bearing 1182 is inserted into the rotation shaft receiving portion 1162c of the orbiting scroll 1162. The outer peripheral surface of the second bush bearing 1182 is in close contact with the inner peripheral surface of the rotation shaft receiving portion 1162c. The second bush bearing 1182 is fixed to the rotation shaft receiving part 1162c.

The second bush bearing 1182 is formed in a hollow cylindrical shape to surround the eccentric portion 1173 of the rotation shaft 1170. The eccentric part 1173 is inserted into the second bush bearing 1182. The rotation shaft 1170 rotates relative to the second bush bearing 1182. The inner circumferential surface of the second bush bearing 1182 and the outer circumferential surface of the eccentric portion 1173 form a bearing surface.

The balance weight 1190 is coupled to the rotation shaft 1170. The balance weight 1190 is installed to offset an eccentric load (or eccentric amount) of the rotation shaft 1170. The balance weight 1190 includes a ring 1190a and an eccentric mass portion 1190b.

The ring 1190a is formed in the shape of a ring surrounding the rotation shaft 1170 so as to be coupled to the rotation shaft 1170. The outer diameter of the ring 1190a is larger than the outer diameter of the rotation shaft 1170.

The eccentric mass portion 1190b extends along an axial direction or a direction parallel to the axial direction from the edge of the ring 1190a. The eccentric mass part 1190b protrudes in the axial direction from an arc having a certain central angle among 360° of the rim of the ring 1190a. Accordingly, the eccentric mass portion 1190b partially surrounds the rotation shaft 1170 at a position spaced apart from the rotation shaft 1170.

Meanwhile, the rear housing 1140 is formed to cover the orbiting scroll 1162. The rear housing 1140 may include an annular protrusion 1143 inserted into the middle housing 1130. The outer peripheral surface of the annular protrusion 1143 is in close contact with the inner peripheral surface of the middle housing 1130.

The rear housing 1140 is disposed on the opposite side of the fixed scroll 1161 with respect to the orbiting scroll 1162. It is formed in the intermediate pressure chamber S3 between the rear housing 1140 and the orbiting scroll 1162. In particular, the rear housing 1140 may include a recess portion 1144 to form an intermediate pressure chamber S3. The recessed portion 1144 is recessed in a direction away from the orbiting plate portion 1162a of the orbiting scroll 1162 to form an intermediate pressure chamber S3 between the fixed plate portion 1161a.

The thrust plate 1191 is disposed between the orbiting scroll 1162 and the rear housing 1140. The thrust plate 1191 may be formed as an annular plate. The thrust plate 1191 forms a thrust surface with the orbiting scroll 1162.

A plurality of holes 1191a for passing the pin 1181 of the anti-rotation mechanism 1180 may be formed in the thrust plate 1191. The plurality of holes 1191a may be formed at a position facing the ring receiving groove 1162d formed in the fixed scroll 1161 in the axial direction of the rotation shaft 1170.

A sealing member 1194 for sealing the intermediate pressure chamber S3 may be installed between the thrust plate 1191 and the orbiting plate portion 1162a of the orbiting scroll 1162. The sealing member 1194 may be formed as an annular O-ring.

Next, the main frame 1120 will be described.

The main frame 1120 is disposed between the compression unit 1160 and the transmission unit 1150 in the axial direction of the rotation shaft 1170. Specifically, the main frame 1120 is coupled to the rear end of the main housing 1110. The main frame 1120, the main housing 1110, and the inverter module 1200 are coupled to each other to form the motor chamber S1 described above.

In addition, the main frame 1120 is coupled to the front end of the middle housing 1130. The main frame 1120 is formed to support the fixed scroll 1161 in the axial direction. The main frame 1120 is installed on the front side of the fixed scroll 1161.

The main frame 1120 includes a discharge part 1121, a base 1121b, a main frame side suction flow path 1121c1, 1121c2, a partition wall 1121d, a sealing member receiving part 1121e, a fixed scroll receiving part 1121f, and communication. It includes a sphere 1121g, an oil separator 1121h, and an oil hole 1121i on the main frame side.

The discharge part 1121 is formed to separate oil from the high-pressure fluid passed from the discharge chamber S2 to the oil separation chamber S4 through the communication port 1121g and discharge the remaining fluid (mainly refrigerant) through the discharge port 1121a. do. For example, the fluid compressed in the compression unit 1160 is discharged to the discharge chamber S2, and the fluid discharged to the discharge chamber S2 passes through the communication port 1121g again to the oil separation chamber S4. Since the discharge port 1121a of the discharge part 1121 is in communication with the oil separation chamber S4 and the discharge chamber S2, the high-pressure fluid may be discharged to the outside of the electric compressor 1000 through the discharge port 1121a.

The base 1121b is formed in a circular plate shape. The rim of the base 1121b is coupled to the rear end of the main housing 1110 to seal the motor chamber S1. And the rim of the base 1121b is coupled to the front end of the middle housing 1130.

The main frame-side suction flow paths 1121c1 and 1121c2 are configured to supply the fluid to be compressed to the compression chamber from the transmission unit 1150 side. The main frame side suction passages 1121c1 and 1121c2 are formed as holes penetrating the base 1121b in the axial direction.

The main frame side suction passages 1121c1 and 1121c2 may be formed at positions facing the fixed scroll side suction passages 1161f1 and 1161f2 in the axial direction. For example, the main frame side suction passages 1121c1 and 1121c2 may be formed in plural, and the plurality of main frame side suction passages 1121c1 and 1121c2 are centered on a fixed scroll receiving portion 1121f formed at the center of the base 1121b. As such, it may be formed on opposite sides of each other in the radial direction of the rotation shaft 1170.

In addition, the main frame side suction passages 1121c1 and 1121c2 may be formed between the outer rim of the discharge chamber S2 and the outer rim of the main frame 1120 in the radial direction of the rotation shaft 1170. The outer rim of the discharge chamber S2 is formed by a partition wall 1121d to be described later, and the outer rim of the main frame 1120 corresponds to the outer rim of the base 1121b.

The main frame 1120 and the fixed scroll 1161 form a discharge chamber S2. The discharge chamber S2 refers to a region in which the compressed high-pressure fluid is discharged from the compression unit 1160. At least one of the main frame 1120 and the fixed scroll 1161 is provided with a partition wall 1121d for forming an outer edge of the discharge chamber S2.

The partition wall 1121d protrudes from the base 1121b of the main frame 1120 toward the fixed scroll 1161 in an annular shape. The outer diameter of the partition wall 1121d is smaller than the outer diameter of the base 1121b. The partition wall 1121d has a cross section in the form of a closed curve to isolate the discharge chamber S2 from the main frame side suction passages 1121c1 and 1121c2 and the fixed scroll side suction passages 1161f1 and 1161f2.

Since the rotation shaft 1170 penetrates the center of the main frame 1120 and the fixed scroll 1161, the discharge chamber S2 is formed in an annular shape around the rotation shaft 1170. Accordingly, in the radial direction of the rotation shaft 1170, the discharge chamber S2 is formed around the periphery, and the suction passages 1121c1, 1121c2, 1161f1, and 1161f2 are formed around the discharge chamber S2.

The sealing member accommodating portion 1121e is formed at an end portion of the partition wall 1121d in the axial direction. The sealing member accommodating portion 1121e may be formed in a closed curve shape along the cross-section of the partition wall 1121d. The sealing member accommodating part 1121e is formed by being recessed in the axial direction at the end of the partition wall 1121d. Annular sealing members 1192, 1193, 1194, and 1195 are inserted into the sealing member accommodating part 1121e to seal the discharge chamber S2. The sealing member 1195 may be formed of an O-ring.

The partition wall 1121d is not necessarily formed on the main frame 1120, but may be formed on the fixed scroll 1161. In this case, the sealing member accommodating portion 1121e is also formed on the fixed scroll 1161.

The fixed scroll receiving portion 1121f is formed in the center of the base 1121b. The fixed scroll accommodating portion 1121f protrudes in an annular shape from the base 1121b toward the transmission portion 1150. The fixed scroll receiving portion 1121f may be formed in a hollow cylindrical shape to surround the rotating shaft receiving portion 1161d inserted into the fixed scroll receiving portion 1121f. A sealing member 1192 may be installed on the outer circumferential surface of the rotating shaft receiving portion 1161d.

The communication port 1121g is formed to communicate the discharge chamber S2 and the oil separation chamber S4 with each other. The communication port 1121g is formed in the base 1121b, and is formed as a hole opened toward the discharge chamber S2. The communication ports 1121g may be formed in plural, and the plurality of communication ports 1121g may be formed at positions spaced apart from each other. The high-pressure fluid discharged from the compression chamber to the discharge chamber S2 flows from the discharge chamber S2 to the oil separation chamber S4 through the communication port 1121g.

The oil separator 1121h is formed to separate oil from the fluid flowing from the discharge chamber S2 to the oil separation chamber S4. The oil separator 1121h is formed to separate a gaseous refrigerant and a liquid oil from each other by using a difference in centrifugal force in a rotating fluid.

The oil separation chamber S4 is formed to collect oil separated by the oil separator 1121h. The oil separation chamber S4 is formed under the oil separator 1121h. Accordingly, the refrigerant separated by the oil separator 1121h is discharged to the outside of the electric compressor 1000 through the discharge unit 1121, and the oil is collected in the oil separation chamber S4.

The main frame side oil hole 1121i is provided along the axial direction to supply the oil collected in the oil separation chamber S4 to the fixed scroll side oil hole 1161h and the fixed scroll side oil supply passage 1161i of the fixed scroll 1161. It penetrates through one side of the main frame 1120. Here, the meaning of penetrating through one side of the main frame 1120 means that in the axial direction of the rotation shaft 1170, the base 1121b penetrates only toward the fixed scroll 1161 and does not penetrate toward the electric part 1150.

The main frame side oil hole 1121i is formed in a position facing each other with the fixed scroll side oil hole 1161h in the axial direction of the rotation shaft 1170. The main frame side oil hole 1121i is formed between the outer rim of the discharge chamber S2 and the outer rim of the main frame 1120 in the radial direction of the rotation shaft 1170. Here, the outer edge of the discharge chamber S2 means the partition wall 1121d, and the outer edge of the main frame 1120 means the outer edge of the base 1121b.

In order to supply oil, the main frame side oil hole 1121i and the fixed scroll side oil hole 1161h must be connected to each other. On the other hand, the fixed plate portion 1161a of the fixed scroll 1161 and the base 1121b of the main frame 1120 must be spaced apart from each other to form the discharge chamber S2. Therefore, in order for the main frame side oil hole 1121i and the fixed scroll side oil hole 1161h to be connected to each other, at least one of the fixed scroll 1161 and the main frame 1120 must have a protrusion protruding in the axial direction toward the other side. do.

If the protrusion is formed in the main frame 1120, the main frame side oil hole 1121i is formed in the protrusion. And the protrusion is in close contact with the fixed plate portion 1161a. Accordingly, the main frame side oil hole 1121i and the fixed scroll side oil hole 1161h may be connected to each other.

Conversely, when the protrusion is formed in the fixed scroll 1161, the fixed scroll side oil hole 1161h is formed in the protrusion. And the protrusion is in close contact with the base 1121b. Accordingly, the main frame side oil hole 1121i and the fixed scroll side oil hole 1161h may be connected to each other.

Since the sidewall portion 1161c of the fixed scroll 1161 may protrude from the fixed plate portion 1161a to be in close contact with the base 1121b, the sidewall portion 1161c may serve as the protrusion. 3 shows a configuration in which the fixed scroll-side oil hole 1161h is formed in the side wall 1161c of the fixed scroll 1161.

Meanwhile, the anti-rotation mechanism 1180 is formed to rotate the orbiting scroll 1162. Without the anti-rotation mechanism 1180, the orbiting scroll 1162 would rotate by the driving force transmitted by the rotation shaft 1170. The anti-rotation mechanism 1180 prevents the orbiting scroll 1162 from rotating and causes the orbiting scroll 1162 to rotate.

The anti-rotation mechanism 1180 may include a pin 1181 and a ring 1182. Each of the pin 1181 and the ring 1182 may be provided in plural. As shown, each of the pins 1181 and 6 rings 1182 may be provided. However, it is not limited thereto, and may be provided in different numbers depending on the design. It can be different.

The plurality of pins 1181 may be provided at the same position in the radial direction based on the axial center of the rotation shaft 1172. In addition, the plurality of rings 1182 may be provided at the same position in the radial direction with respect to the center of the turning plate portion 1162a. That is, the pin 1181 and the ring 1182 may be disposed on a virtual circumference, respectively. In addition, the pin 1181 and the ring 1182 may be provided to be spaced apart by the same distance in the circumferential direction.

As shown, the pin 1181 may be installed on the rear housing 1140. More specifically, the pin 1181 may be installed by being press-fitted onto one surface of the rear housing 1140 facing the second surface of the orbiting scroll 1162. However, as will be described later, in other application examples, the pin 1181 may be installed on the main frame.

The pin 1181 may be formed in a cylindrical shape having a length relatively longer than a diameter. At least a portion of the pin 1181 may be fixed by being inserted into one surface of the rear housing 1140. At this time, the pin 1181 may be provided in parallel with the axial direction. That is, it may be fixed to be perpendicular to one surface of the rear housing 1140.

Another part of the pin 1181 may be provided to protrude from one surface of the rear housing 1141, and the ring 1182 may be slidably coupled to the protruded part of the pin 1181.

The ring 1182 may be formed in an annular ring shape. That is, the ring 1182 is formed in a circular shape, and is formed to open both sides. Here, both open sides of the ring 1182 may be arranged to face the front side and the rear side of the compressor. However, the present invention is not limited thereto, and the ring 1182 may be formed such that only one side thereof is opened, as in an embodiment to be described later.

Here, the pin 1181 is inserted into the open side of the ring 1182. Meanwhile, the ring 1182 is coupled to the orbiting scroll 1162 and moves together by the movement of the orbiting scroll 162. That is, when the rotational force of the rotating shaft 1172 is transmitted to the orbiting scroll 1162 and the orbiting scroll 1162 is rotated, the ring 1182 moves in the direction of rotation of the orbiting scroll 1162 and the orbiting scroll 1162. .

At this time, since the pin 1181 comes into contact with the inner circumferential surface 1182b of the ring 1182, the ring 1182 is restricted from moving in the rotational direction of the orbiting scroll 1162, and slides with respect to the pin 1181. do. Accordingly, the orbiting scroll 1162 is also unable to rotate based on the center of the rotation shaft 1172 together with the rotation shaft 1172 and performs a orbiting motion.

Regarding the ring 1182, when the orbiting scroll 1162 moves, the pin 1181 slides along the inner circumferential surface 1182b of the ring 1182 and revolves based on the center of the ring 1182. .

Meanwhile, the ring 1182 is coupled to the orbiting scroll 1162. More specifically, the ring 1182 is coupled in a state received in the ring receiving groove 1162a of the orbiting scroll 1162. The ring 1182 may be fixedly coupled by press-fitting in a manner that is coupled to the ring receiving groove 1162a, but when the ring 1182 is press-fitted and coupled to the orbiting scroll 1162, it is transformed into the orbiting scroll 1162 Will occur.

Accordingly, the ring 1182 and the ring receiving groove 1162d may be formed to form a predetermined gap between the outer circumferential surface 1182a of the ring 1182 and the inner circumferential surface 1162d1 of the ring receiving groove 1162d. In this case, when assembling the compressor, the ring 1182 is separated from the ring receiving groove 1162d.

More specifically, due to the characteristics of the compressor assembly process, the compressor is assembled with the orbiting wrap 1162b of the orbiting scroll 1162 facing upward, and the ring 1182 is separated from the ring receiving groove 1162d by gravity. I have to. In addition, the assembling process is complicated due to the characteristic that the pin 1181 must be assembled to be inserted into the ring 1182.

Hereinafter, a structure capable of preventing the ring 1182 from being separated from the ring receiving groove 1162d during assembly of the compressor will be described without causing deformation in the orbiting scroll 1162.

Hereinafter, an anti-rotation mechanism 1180 according to an embodiment of the present invention will be described with reference to the drawings.

Figure 4 is a view showing the coupling relationship between the orbiting scroll and the pin and ring according to the present invention, Figure 5a is a view showing an enlarged cross-section of the pin and ring is installed according to an embodiment of the present invention, Figure 5b is shown in Figure 5a It is a view from above of the old ring.

The ring 1182 of the anti-rotation mechanism 1180 according to an embodiment of the present invention may be screwed into the ring receiving groove 1162d to be coupled.

More specifically, a thread 1182a1 is formed on the outer circumferential surface 1182a of the ring 1182, and a screw groove 1162d1 corresponding to the thread 1182a1 may be formed on the inner circumferential surface of the ring receiving groove 1162d. Alternatively, a thread may be formed on the inner circumferential surface of the ring receiving groove 1162d, and a screw groove corresponding thereto may be formed on the outer circumferential surface of the ring 1182.

In general, since the thread and the screw groove can be formed through cutting, deformation of the orbiting scroll can be prevented. In addition, since the ring 1182 is prevented from being separated from the ring receiving groove 1162d by screwing, assembly of the compressor may be facilitated.

However, when the ring 1182 is coupled to the orbiting scroll 1162, the ring 1182 must be screwed into the ring receiving groove 1162d by rotating with respect to the orbiting scroll 1162, but the surface of the ring 1182 is Since it is formed to be relatively slippery, it is difficult to rotate the ring 1182. This is because the ring 1182 is formed to have a surface having a relatively low coefficient of friction due to the structural characteristic of the pin 1181 contacting the inner circumferential surface 1182b of the ring 1182 and performing slide movement.

Accordingly, first and second fastening grooves 1182c1 and 1182c2 for screwing the ring 1182 may be formed on the inner circumferential surface 1182b of the ring 1182.

The first fastening groove 1182c1 is formed by being recessed from one side of the inner circumferential surface 1182b of the ring 1182, and the second fastening groove 1182c2 may be formed at a position facing the first fastening groove 1182c1. have. That is, the first fastening groove 1182c1 and the second fastening groove 1182c2 may be formed at positions symmetrical with respect to the center of the ring 1182.

Accordingly, after inserting a tool such as a flat screwdriver between the first fastening groove 1182c1 and the second fastening groove 1182c2, and rotating the ring 1182, the ring 1182 is inserted into the ring receiving groove 1162d. Can be easily fastened to.

On the other hand, since the screwdriver is generally formed in a rectangular shape in cross section, the first fastening groove 1182c1 and the second fastening groove 1182c2 will be formed to form a hexahedral space to correspond to both ends of the flat screwdriver. I can.

More specifically, the first fastening groove 1182c1 and the second fastening groove 1182c2 intersect the inner circumferential surface 1182b of the ring 1182 and have both sides (first and second surfaces) formed to face each other. Can include. Here, both side surfaces (first and second surfaces) facing each other may extend parallel to each other. Further, it is bent at both sides, and may include an inner surface toward the center of the ring 1182. In other words, the inner surface extends in a direction crossing both sides, and may be connected to form an inner edge together with both sides.

That is, the first fastening groove 1182c1 and the second fastening groove 1182c2 can form a square-shaped space defined by both side surfaces and inner surfaces. The end of the screwdriver is accommodated in the square-shaped space, and according to the rotation of the screwdriver, the ring 1182 is rotated to be screwed into the ring receiving groove 1162d.

On the other hand, the first fastening groove 1182c1 and the second fastening groove 1182c2 may be formed to extend in the axial direction so as to sufficiently receive the torque of a screwdriver. In other words, the first fastening groove 1182c1 and the second fastening groove 1182c2 may be formed to extend in the longitudinal direction of the ring 1182.

However, when the first fastening groove 1182c1 and the second fastening groove 1182c2 extend to correspond to the axial length of the ring 1182, the pin 1181 is the first fastening groove 1182c1 and the second fastening groove. Damage may occur by bumping the edge of (1182c2). Accordingly, the first fastening groove 1182c1 and the second fastening groove 1182c2 may extend by a preset length in the axial direction.

In addition, as a method to prevent damage caused by the pin 1181 colliding with the corners of the first and second fastening grooves 1182c1 and 1182c2, the first fastening groove 1182c1 and the second fastening groove ( 1182c2) can be rounded. That is, both sides (first and second surfaces) of the first and second fastening grooves 1182c1 and 1182c2 may be connected to the inner circumferential surface 1182b to be round.

Meanwhile, FIG. 6A is a view showing a longitudinal cross-section of a ring according to a modified example of an embodiment of the present invention, and FIG. 6B is a view viewed from above of the ring shown in FIG. 6A.

According to a variation of the embodiment, unlike the ring 1182 of the above-described embodiment, the ring 2182 according to the present embodiment may be formed such that only one side is open. In other words, only the direction toward the pin can be opened.

More specifically, the ring 2182 may include a sidewall facing and in contact with the ring receiving groove 1162d, and an inner wall formed to intersect at the sidewall to block an open end of the sidewall.

Here, as in the above-described embodiment, a thread corresponding to the screw groove formed on the inner peripheral surface of the ring receiving groove 1162d may be formed on the outer peripheral surface 2182a of the side wall. The pin 1181 is in contact with the inner circumferential surface 2182b of the side wall, so that it can be slid.

Meanwhile, the inner wall 2182c may include an inner surface facing the end surface of the pin 1181. Here, the fastening groove 2182c1 may be formed on the inner surface of the inner wall 2182c. The fastening groove 2182c1 is formed to be recessed in the inner surface, and may be formed to extend along any one direction.

A flat screwdriver (scrwdriver) is inserted into the fastening groove 2182c1, so that the ring 1182 can be rotated. Accordingly, the fastening groove 2182c1 may be formed in a rectangular shape so as to correspond to the cross section of the flat screwdriver (scrwdriver).

In this embodiment, the end surface of the pin 1181 may be provided to be spaced apart from the inner surface of the inner wall 2182c. Accordingly, damage by rubbing the pin 1181 into the fastening groove 2182c1 can be prevented.

On the other hand, Figure 7 is a view showing another application example of the pin and ring according to an embodiment of the present invention.

The pin-and-ring type anti-rotation mechanism 1180 according to the present invention is applicable not only to the above-described compressor, but also to other compressors.

As shown, an orbiting scroll 3162 is provided between the main frame 3120 and the fixed scroll 3161, and the orbiting scroll 3162 is supported in the axial direction by the main frame 3120. The anti-rotation mechanism 1180 according to the embodiment and its modifications may be applied. That is, in this application example, unlike previously described, the pin 1181 may be installed on the main frame 3120.

Meanwhile, FIG. 8A is a view showing a state in which a pin and ring according to another embodiment of the present invention is installed, and FIG. 8B is a view showing the ring of the pin and ring shown in FIG. 8A from above.

In this embodiment, unlike the above-described embodiment, a structure in which the ring 4182 can be assembled while being adhered to the second surface of the orbiting scroll 1162 due to the viscosity of oil is proposed.

Specifically, the ring 4182 may include a first portion 4182a inserted into the ring receiving groove 1162d and a second portion 4182b formed to cover the second surface of the orbiting scroll 1162.

The first portion 4182a may be inserted into the ring receiving groove 1162d, and may be formed to slide by contacting the pin 4181 to the inner circumferential surface.

The second portion 4182b may be formed to cover at least a portion of the second surface of the orbiting scroll 1162. Here, the second part 4182b may be formed in an overall circular shape, and may also serve as a thrust plate to reduce friction with the rear housing 1140.

In such a structure, after applying a predetermined oil to the oil application area D.S of the second portion 4182b and adhering it to the second surface of the orbiting scroll 1162, assembly of the compressor may proceed. Accordingly, when the compressor is assembled, the ring is restricted from being separated into the ring receiving groove without causing deformation to the orbiting scroll, so that assembly of the compressor may be facilitated.

Meanwhile, the oil application region D.S of the second portion 4182b may be formed to be concave. More specifically, an oil receiving portion in which at least a portion of oil is accommodated may be formed between the second surface of the orbiting scroll 1162 and the second portion 4182b of the ring 4182. The oil receiving portion may be formed by an oil reservoir surface formed concave on a surface of the second portion 4182b of the ring 4182 that faces the orbiting scroll 1162.

Meanwhile, FIG. 9A is a view showing an application example of a pin and ring according to a modified example of another embodiment of the present invention, and FIG. 9B is a view showing a ring of the pin and ring shown in FIG. 9A from above.

An orbiting scroll 3162 shown in FIG. 7 with a ring 4182 according to the previous embodiment is provided between the main frame 3120 and the fixed scroll 3161, and the orbiting scroll 3162 is axially directed by the main frame 3120. This is an example applied to a structure supported by.

In this structure, the rotating shaft 3171 passes through the main frame 3120 and is eccentrically coupled to the orbiting scroll 3162. In this case, the ring 5182 may include a through groove 5182b1 formed in the second portion so that the rotation shaft 3171 can be coupled to the orbiting scroll 3162.

The rotation shaft 371 may pass through the through hole 5182b1 and may be coupled to the orbiting scroll 3162. In the present embodiment, the remaining area except for the through hole 5182b1 may correspond to the oil application area D.S.

That is, when assembling the compressor, oil is applied to one surface facing the orbiting scroll 3162 of the second part 5182b, that is, the oil application area DS, and adhered to the orbiting scroll 3162, and then the assembly process of the compressor. You can proceed.

What has been described above are only examples for implementing the scroll compressor according to the present invention, and the present invention is not limited to the above embodiments, and the above embodiments are all or part of each of the embodiments so that various modifications can be made. May be configured by selectively combining. As claimed in the following claims, any person of ordinary skill in the field to which the present invention belongs will have the technical idea of the present invention to the extent that various changes can be implemented within the scope not departing from the gist of the present invention. .

Claims (12)

Rotating shaft;
A first scroll provided on one side of the rotation shaft;
A second scroll engaged with the first scroll to form a compression chamber between the first scroll and a ring receiving groove formed on a surface opposite to the surface facing the first scroll;
At least a portion of the pin is positioned in the ring receiving groove to guide the movement of the second scroll, and a ring positioned between the pin and the ring receiving groove, so that the second scroll is rotated with respect to the first scroll. It includes a pin and ring formed to be
The ring is an electric compressor, characterized in that coupled by screwing into the ring receiving groove. The method of claim 1,
A screw groove is formed on the inner circumferential surface of the ring receiving groove,
An electric compressor, characterized in that a thread corresponding to the screw groove is formed on an outer circumferential surface of the ring. The method of claim 2,
The ring,
A first fastening groove formed by being recessed on one side of the inner circumferential surface of the ring; And
An electric compressor comprising a second fastening groove formed in a position facing the first fastening groove. The method of claim 3,
The first and second fastening grooves are electric compressors, characterized in that extending in the axial direction of the rotation shaft from the inner circumferential surface of the ring. The method of claim 4,
An electric compressor, characterized in that the axial length of the first and second fastening grooves is smaller than the axial length of the ring. The method of claim 3,
The first and second fastening grooves each intersect the inner circumferential surface of the ring and include first and second surfaces facing each other,
The first and second surfaces are respectively connected to the inner circumferential surface in a rounded manner. The method of claim 2,
The ring,
A side wall on which the thread is formed on an outer peripheral surface;
And an inner wall crossing the sidewall and including an inner surface facing the end surface of the pin,
The inner wall is formed by being recessed in the inner surface, the electric compressor comprising a fastening groove extending in a direction on the inner surface. The method of claim 7,
The electric compressor, characterized in that the end surface of the pin is spaced apart from the inner surface. The method according to any one of claims 1 to 8,
The electric compressor,
Further comprising a main frame provided on the opposite side of the first scroll with the second scroll interposed therebetween, and supporting the second scroll in an axial direction,
The pin is an electric compressor, characterized in that installed on one surface of the main frame facing the second scroll. Rotating shaft;
A first scroll provided on one side of the rotation shaft;
A second scroll engaged with the first scroll to form a compression chamber between the first scroll and a ring receiving groove formed on a second surface opposite to the first surface facing the first scroll;
At least a portion of the pin is positioned in the ring receiving groove to guide the movement of the second scroll, and a ring positioned between the pin and the ring receiving groove, so that the second scroll is rotated with respect to the first scroll. It includes a pin and ring formed to make,
The ring,
A first portion inserted into the ring receiving groove and slidably moved with respect to the pin; And
And a second portion formed to cover at least a portion of the second surface,
And the second portion is formed to protrude in the axial direction from the first portion. The method of claim 10,
The second part,
And an oil reservoir surface concavely formed on a surface of the second portion facing the second scroll to form an oil receiving portion between the second portion and the second scroll. The method of claim 10,
The rotation shaft is formed to penetrate the second scroll and supported in a radial direction by the first scroll,
The second part comprises a through hole in which at least a part of the rotation shaft is provided.

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