KR102232270B1 - Motor operated compressor - Google Patents

Abstract

The electric compressor of the present invention includes a drive motor having a stator and a rotor; A fixed scroll fixed to one side of the drive motor; An orbiting scroll disposed between the driving motor and the fixed scroll to form the fixed scroll and a compression chamber, and for orbiting motion by a rotational force provided from the drive motor; And an eccentric portion formed to be eccentrically coupled to the orbiting scroll, and including a rotation shaft connected to the rotor and the orbiting scroll to transmit a rotational force provided from the drive motor to the orbiting scroll, wherein the orbiting scroll is cumbersome. A rotation shaft coupling portion formed to surround the eccentric portion in a radial direction of the rotation shaft; And a cover part coupled to the rotation shaft coupling part along a circumference and disposed between the eccentric part and the fixed scroll so as to cover the eccentric part in the axial direction of the rotation shaft, wherein the fixed scroll includes the fixed scroll A fluid discharge passage penetrating in the axial direction of is formed, and the fluid discharge passage is formed at a position overlapping with the cover portion in the axial direction of the rotation shaft.

Description

Electric compressor {MOTOR OPERATED COMPRESSOR}

The present invention relates to an electric compressor driven by a motor.

A compressor is a device that increases pressure by compressing a fluid, and is classified into a mechanical type using an engine as a driving source and an electric type using a motor as a driving source.

As an electric compressor, a scroll compression method suitable for operation with a high compression ratio is known. In the inside of the sealed casing (or housing) of an electric compressor having a scroll compression method (hereinafter, abbreviated as an electric compressor in this specification), an electric unit composed of a drive motor is installed. And a compression unit consisting of a fixed scroll and an orbiting scroll is installed on one side of the electric unit. The electric part and the compression part are connected to each other by a rotating shaft. The rotational force provided by the electric unit is transmitted to the compression unit through the rotating shaft. In addition, the compression unit compresses a fluid to be compressed, such as a refrigerant, by the rotational force transmitted through the rotation shaft.

Compressors having a relatively low operating compression ratio, such as for home use, are generally known to have a structure that prevents overpressure in a compression chamber by discharging a fluid to be compressed at an intermediate pressure through a bypass flow path. Here, the intermediate pressure means a pressure between the pressure before compression (suction pressure) and the pressure after compression (discharge pressure) of the fluid to be compressed. For example, Korean Patent Laid-Open Publication No. 10-2014-0114212 (2014.09.26.) discloses a scroll compressor having a bypass means.

The bypass flow path 149 as disclosed in the patent document differs only in that it is discharged at a lower pressure than the discharge pressure, and there is no difference in its practical function from the discharge port for discharging the discharge pressure fluid. Therefore, the problem of a decrease in instruction efficiency caused by a shortage of the discharge port area can be prevented simply by increasing the number of bypass flow paths. Here, the indicated efficiency refers to the ratio of A and B when the theoretical power is A, and the sum of the theoretical power and the indicated loss power (loss power due to leakage of working gas) is B.

In contrast, in a compressor having a relatively high driving compression ratio, such as for automobiles, if the number of bypass flow paths is arbitrarily increased, the fluid to be compressed does not reach a desired discharge pressure. Therefore, in a compressor operated at a high compression ratio, unlike a compressor operated at a low compression ratio, the problem of a shortage of the discharge port area and a decrease in instruction efficiency cannot be solved by the method of increasing the number of bypass flow paths.

In addition, forming a plurality of bypass flow paths in the scroll acts as a factor to deteriorate the manufactureability of the compressor, and may lead to an increase in the price of the compressor. Furthermore, since the pressure of the fluid to be discharged is different according to the position of the bypass flow path, an increase in the number of the bypass flow paths causes a problem in that it is difficult to discharge the fluid to be compressed at the correct desired discharge pressure.

On the other hand, one of ordinary skill in the art may consider a method of increasing the size of the discharge port in order not to depend on the method of increasing the number of bypass flow paths. However, in order to support the two-point support in the compression unit for the two-point support for stable rotation, the rotary shaft must completely penetrate the rotary shaft coupling portion of the orbiting scroll and be inserted into the fixed scroll. In this structure, there is a new problem that the fluid to be discharged from the compression chamber to the discharge chamber flows backwards between the rotation shaft coupling portion of the orbiting scroll and the rotation shaft.

U.S. Patent Publication US 9,512,840 B2 (2016.12.06.) discloses a structure capable of preventing a fluid from flowing backward between the rotation shaft coupling portion and the rotation shaft by blocking one end of the rotation shaft with a orbiting scroll. However, the structure disclosed in the patent document does not disclose the relationship between the discharge port and the structure blocking one end of the rotating shaft, and the structure of the patent document cannot solve the problem of the shortage of the discharge port area and the decrease in instruction efficiency.

Furthermore, the structure disclosed in the above patent document does not explicitly disclose a structure for lubricating oil around the rotation shaft, so there remains a question about how to lubricate the rotation shaft in a structure that blocks one end of the rotation shaft.

An object of the present invention is to provide a motor-driven compressor having a structure capable of sufficiently securing an area of a discharge port without depending on a bypass flow path, thereby preventing a decrease in instruction efficiency.

An object of the present invention is to provide an electric compressor having a structure capable of unifying a discharge port to improve manufactureability of a compressor, reduce manufacturing cost of a compressor, and discharge a fluid to be compressed at an accurate desired discharge pressure.

An object of the present invention is to ensure that the rotating shaft, which was supported only by two points in the compression unit, is supported by one point at the compression unit and the transmission unit, so that the rotation axis can be stably rotated without completely penetrating the rotation axis coupling unit of the orbiting scroll. The purpose is to propose an electric compressor that does not cause backflow of fluid even when a structure with one end closed (or a structure with one end closed) is introduced in the rotation shaft coupling part and the discharge port is enlarged than before.

An object of the present invention is to provide an electric compressor capable of solving the problems of shortage of discharge port area and decrease in instruction efficiency by structurally defining a relationship between a structure blocking one end of a rotating shaft and a discharge port (fluid discharge flow path). .

Furthermore, the present invention is to provide a structural solution to how to lubricate the rotating shaft in a structure that blocks one end of the rotating shaft.

The electric compressor of the present invention includes a fixed scroll and an orbiting scroll, and the orbiting scroll includes a cover portion disposed between the rotating shaft and the fixed scroll so as to cover one end of the rotating shaft in the axial direction. In the fixed scroll, a fluid discharge flow path penetrating the fixed scroll in the axial direction of the rotation shaft is formed, and in order to sufficiently secure the area of the discharge port without depending on the bypass flow path, the fluid discharge flow path is provided with the cover in the axial direction of the rotation shaft. It is formed in a position overlapping with the wealth.

The orbiting scroll includes a rotation shaft coupling portion formed to surround one end of the rotation shaft in a radial direction of the rotation shaft.

An eccentric portion formed to be eccentrically coupled to the orbiting scroll is formed at one end of the rotating shaft.

The rotation shaft coupling portion is formed to surround the eccentric portion in the radial direction of the rotation shaft.

The cover portion is coupled to the rotation shaft coupling portion along the circumference of the cover portion.

The cover portion is disposed between the eccentric portion and the fixed scroll so as to cover the eccentric portion in the axial direction of the rotation shaft.

The electric compressor is driven by a drive motor, the drive motor having a stator and a rotor.

The fixed scroll is fixed to one side of the drive motor.

The orbiting scroll is disposed between the drive motor and the fixed scroll to form the fixed scroll and a compression chamber.

The orbiting scroll rotates by a rotational force provided from the drive motor.

The rotation shaft is connected to the rotor and the orbiting scroll to transmit rotational force provided from the drive motor to the orbiting scroll.

The rotation shaft has a first end and a second end, and the rotation shaft is supported by a compression unit and an electric unit (drive motor) by one point based on a radial direction of the rotation shaft. The first stage is disposed on the opposite side of the orbiting scroll based on the driving motor. The first end is supported in a radial direction of the rotation shaft by a first bearing surrounding the rotation shaft. The eccentric portion is formed in the second end. The rotation shaft is supported in a radial direction of the rotation shaft by a second bearing surrounding the rotation shaft between the eccentric portion and the drive motor. According to this structure, a structure with one end closed (or a structure with one end closed) can be introduced into the rotation shaft coupling portion of the orbiting scroll.

The electric compressor further includes a main housing. The main housing has a hollow column shape.

The fixed scroll includes a fixed hard plate. The fixed plate part is fixed to the inner circumferential surface of the main housing along the circumference.

The fixed scroll includes a fixed wrap. The fixed wrap protrudes from the fixed plate portion toward the orbiting scroll along the vortex.

The present invention provides a position of the fluid discharge passage so that the fluid discharge passage can be unified, and the fluid discharge passage penetrates the fixed plate portion between the center of the fixed plate portion and the innermost portion of the vortex.

The present invention provides the position of the fluid discharge passage so that the fluid discharge passage can be unified, and when the center of the fixed plate portion is referred to as a first point and the innermost part of the vortex is referred to as a second point, the fluid discharges The flow path is formed in an imaginary circle centering on the first point and having a radius from the first point to the second point.

The orbiting scroll may include an orbiting hard plate; And a orbiting wrap protruding from the orbiting hard plate portion toward the fixed scroll along the vortex.

The rotation shaft coupling portion is formed on the innermost portion of the orbiting wrap.

The cover portion is formed at a position farthest from the turning plate portion in the axial direction of the rotation shaft.

The fluid discharge passage is formed at a position partially overlapping with the cover part based on the axial direction of the rotation shaft.

While the orbiting scroll maintains the overlapping state of the cover portion and the fluid discharge passage while the orbiting scroll rotates, the overlapping area of the cover portion and the fluid discharge passage repeatedly increases and decreases.

During the orbiting movement of the orbiting scroll, the rotation shaft coupling portion and the fluid discharge passage maintain an overlapping state in the axial direction of the rotation shaft.

The compression chamber includes a first compression chamber and a second compression chamber.

At a start point of discharging the fluid compressed in the first compression chamber and the second compression chamber, the fluid discharge passage overlaps both the first compression chamber and the second compression chamber in an axial direction of the rotation shaft.

The rated operation compression ratio of the electric compressor is 5 or more.

An oil guide flow path is formed in the cover portion to pass through the cover portion in the axial direction of the rotation shaft. The oil guide passage and the fluid discharge passage are formed at positions not overlapping with each other in the axial direction of the rotation shaft.

Only one fluid discharge passage may be formed in the fixed scroll.

According to the structure provided by the present invention, since a sufficient discharge port area is secured with only one fluid discharge channel, problems of a shortage of discharge port area and a decrease in instruction efficiency can be solved without relying on an increase in the number of bypass channels. Therefore, the compressor of the present invention is a structure suitable for an electric compressor operated at a high compression ratio.

The compression ratio is a comparison between the suction pressure and the discharge pressure of the fluid to be compressed, and the high compression ratio in the present invention means 4 or more, preferably 5 or more. For example, the structure of the present invention is suitable to be applied to an electric compressor operated with a compression ratio of 4 or more, preferably 5 or more.

If the problem of the discharge port area does not occur with only one fluid discharge passage in the fixed scroll, it is possible to improve the manufactureability of the compressor. This is because the process for forming the bypass flow path may be omitted. Furthermore, if the fluid is discharged with only one fluid discharge passage, the fluid may be discharged with an accurate desired discharge pressure.

In addition, according to the present invention, since a closed structure is introduced around the eccentric portion by the cover portion and the rotation shaft coupling portion, even if the size of the fluid discharge passage is increased, the phenomenon that the fluid to be compressed flows back between the rotation shaft coupling portion and the rotation shaft can be prevented have.

Further, according to the present invention, since the oil guide passage of the cover portion is formed at a position not overlapping with the fluid discharge passage of the fixed scroll, oil can be supplied to the region to be lubricated without backflow of the fluid to be compressed.

1 is a perspective view showing the appearance of the electric compressor proposed in the present invention.
FIG. 2 is an exploded perspective view of the electric compressor shown in FIG. 1 by separating the compression module and the inverter module.
3 is an exploded perspective view of the electric compressor shown in FIGS. 1 and 2.
4 is a cross-sectional view of the electric compressor shown in FIGS. 1 and 2.
5 is a perspective view of the fixed scroll and the orbiting scroll shown in FIG. 3 viewed from different directions.
6 is a cross-sectional view showing a compression chamber formed by a fixed scroll and an orbiting scroll.
7 is a conceptual diagram showing a process of orbiting the orbiting scroll with respect to the fixed scroll.

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 and 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. It 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.

In this section, the appearance of the electric compressor will be described with reference to FIG. 1, and the structure when the compression module and the inverter module of the electric compressor are separated from each other will be described with reference to FIG. In addition, the internal structure of the compression module will be described with reference to FIGS. 3 to 7. In particular, in Figures 3 to 7 will be described in detail the technical features of the present invention mentioned in the previous problem to be solved and the means for solving the problem.

First, Figure 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 to be compressed, 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.

For convenience of explanation, the direction of the electric compressor 1000 may be defined based on the flow of the fluid compressed by the compression module 1100. For example, the side where the intake port 1111 is formed to receive the fluid is defined as the front side of the electric compressor 1000. In addition, the side where the discharge port 1121 is formed to discharge the fluid is defined as the rear side of the electric compressor 1000.

If the direction is defined based on the flow of the fluid compressed by the electric compressor 1000 as described above, one side of the compression module 1100 to which the inverter module 1200 is coupled refers to the front side of the compression module 1100. . Since the fluid to be compressed is introduced into the intake port 1111 and discharged to the discharge port 1121, the inverter module 1200 disposed close to the intake port 1111 may be described as being coupled to the front side of the compression module 1100.

The exterior of the compression module 1100 may be formed by the main housing 1110 and the rear housing 1120.

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 as shown in FIG. 1. Both ends of the main housing 1110 may be opened in whole or in part. For example, the front end of the main housing 1110 may be entirely open, and the rear end of the main housing 1110 may be partially opened. Here, the front end of the main housing 1110 refers to an end coupled to the inverter module 1200. In addition, the rear end of the main housing 1110 refers to an end coupled to the rear housing 1120. The front end and the rear end may be referred to as the first end and the second end, respectively.

In FIG. 1, it is shown that the outer diameter of the main housing 1110 is constant. However, the inner diameter and the outer diameter of the main housing 1110 may not be constant. For example, the front portion and the rear portion of the main housing 1110 may have an outer diameter larger than that of an intermediate portion between the front portion and the rear portion, if necessary.

An intake port 1111 and a mount portion 1112 are formed on the outer circumferential surface of the main housing 1110.

The intake port 1111 corresponds to a flow path for supplying the fluid to be compressed to the internal space of the electric compressor 1000. The circumference of the intake port 1111 may protrude from the outer circumferential surface of the main housing 1110. The intake port 1111 may be connected to a suction pipe (not shown) that supplies a fluid to be compressed to the electric compressor 1000. The intake port 1111 has a shape corresponding to the suction pipe so as to be coupled to the suction pipe.

The mount unit 1112 is a configuration for fixing the electric compressor 1000 to an installation target area. The mount portion 1112 may protrude from the outer peripheral surface of the main housing 1110. For example, the mount part 1112 may protrude along the circumferential direction of the main housing 1110. The mount part 1112 may extend along the tangential direction of the outer peripheral surface of the main housing 1110.

A fastening member coupling hole 1112a capable of coupling with an arbitrary fastening member is formed in the mount portion 1112. The fastening member coupling hole 1112a may be opened toward a tangential direction of the outer circumferential surface of the main housing 1110. The mount unit 1112 may be formed on one side and the other side (up/down or left/right) of the main housing 1110, respectively. For example, in FIG. 1, the mount portions 1112 are formed above and below the main housing 1110, respectively.

The main housing-side fastening part 1113 is a configuration for coupling the compression module 1100 and the inverter module 1200 to each other. The main housing side fastening part 1113 may protrude from the front end of the main housing 1110. The main housing side fastening part 1113 may be formed in plural along the outer peripheral surface of the main housing 1110. The plurality of main housing-side fastening portions 1113 may be disposed to be spaced apart from each other. A fastening hole 1113a for fastening bolts is formed in the fastening part 1113 on the main housing side. The main housing side fastening part 1113 may be bolted to the inverter cover 1220 of the inverter module 1200 through the fastening hole 1113a.

Meanwhile, the rear housing 1120 is coupled to the other side of the main housing 1110. According to the direction defined based on the flow of the fluid compressed by the electric compressor 1000 above, the rear housing 1120 is coupled to the rear end of the main housing 1110. The rear housing 1120 may be formed to cover the rear end of the main housing 1110.

The rear housing 1120 includes a discharge port 1121 and a mount portion 1122.

The discharge port 1121 corresponds to a flow path through which the fluid compressed by the electric compressor 1000 is discharged to the outside. The circumference of the discharge port 1121 may protrude from the outer circumferential surface of the rear housing 1120. The discharge port 1121 may be connected to a discharge pipe (not shown) that supplies the compressed fluid to the downstream device of the refrigeration cycle. The discharge port 1121 has a shape corresponding to the discharge pipe so as to be coupled to the discharge pipe.

The mount part 1122 is formed on an outer surface of the rear side of the rear housing 110. The mount part 1122 may protrude from an outer surface of the rear side of the rear housing 1120. The mount part 1122 may extend in a left-right direction (or vertical direction). A fastening member coupling hole 1122a is formed in the mount part 1122. The mount portion 1122 serves substantially the same as the mount portion 1112 of the main housing 1110.

The main housing 1110 and the rear housing 1120 may be coupled to each other by a plurality of fastening members 1123. The fastening member 1123 is inserted from the rear housing 1120 side toward the main housing 1110 side. A plurality of fastening members 1123 may be installed along the circumference of the rear housing 1120.

Next, the inverter module 1200 will be described.

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 to form a mounting space for circuit components and the like.

The inverter housing 1210 is disposed at the front end of the electric compressor 1000. One surface of the inverter housing 1210 is disposed to face the front of the electric compressor 1000, and the one surface forms an outer wall of the electric compressor 1000. The inverter housing 1210 has a side wall, and the side wall protrudes toward the inverter cover 1220 along an edge of the one surface. The circumference of the inverter housing 1210 may be larger than the circumference of the main housing 1110 due to the size of circuit components such as a printed circuit board disposed in the inverter module 1200.

The inverter cover 1220 is coupled to the inverter housing 1210. The inverter cover 1220 may be formed in a plate shape covering the opening of the inverter housing 1210 and the front end of the main housing 1110. In this case, the edge of the inverter cover 1220 may have a shape corresponding to the sidewall of the inverter housing 1210. However, the inverter cover 1220 is not necessarily formed in a plate shape, and may have a shape corresponding to the inverter housing 1210.

The inverter housing 1210 and the inverter cover 1220 may be coupled to each other by a plurality of fastening members (not shown).

The inverter cover 1220 has a first surface (or a front surface) disposed toward the inverter housing 1210 and a second surface (or a rear surface) disposed toward the main housing 1110. A first surface of the inverter cover 1220 is coupled to the inverter housing 1210, and a second surface of the inverter cover 1220 is coupled to the main housing 1110.

The inverter cover 1220 is provided with a power connector 1241 and a communication connector 1242. The power connector 1241 and the communication connector 1242 are formed to be physically and electrically connected to different mating connectors (not shown), respectively. The power connector 1241 is formed to transmit power supplied from a mating connector to a circuit component or the like. The communication connector 1242 electrically transmits a control command or the like transmitted from the outside to a circuit component or the like so that the electric compressor 1000 is driven according to the control command.

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

FIG. 2 is an exploded perspective view of the electric compressor 1000 shown in FIG. 1 by separating the compression module 1100 and the inverter module 1200.

When the compression module 1100 and the inverter module 1200 are separated from each other, the motor chamber S1 is exposed through the front end 1110a of the main housing 1110 in the compression module 1100. The motor room S1 refers to a space in which the drive motor 1130 is installed, and corresponds to a space in which the fluid to be compressed is supplied through the intake port 1111.

When the compression module 1100 and the inverter module 1200 are separated from each other, the inverter module 1200 exposes the rear surface of the inverter cover 1220 that was covered by the main housing 1110. The rear surface of the inverter cover 1220 that was covered by the main housing 1110 corresponds to one side wall of the motor chamber S1.

The motor chamber S1 is formed by coupling the main housing 1110 and the inverter cover 1220. A sealing member 1191 such as an O-ring (refer to FIG. 4) may be installed along the coupling position of the main housing 1110 and the inverter cover 1220 to seal the motor chamber S1. This sealing member 1191 is not shown in FIG. 2, but is shown in FIG. 4.

The drive motor 1130 corresponding to the electric unit is installed in the motor chamber S1. The drive motor 1130 includes a stator 1131 and a rotor 1132.

The stator 1131 is installed along the inner circumferential surface of the main housing 1110 and is fixed to the inner circumferential surface of the main housing 1110. The stator 1131 is inserted and fixed to the main housing 1110 by shrink fit (or hot press fit). Therefore, setting the insertion depth of the stator 1131 inserted into the main housing 1110 to be small (or shallow) is advantageous in securing the ease of installation work of the stator 1131. Furthermore, setting the insertion depth of the stator 1131 to be shallow is also advantageous in maintaining the concentricity of the stator 1131 during the shrink fit process.

The rotor 1132 is installed in an area surrounded by the stator 1131. The rotor 1132 rotates by electromagnetic interaction with the stator 1131.

The rotation shaft 1160 is coupled to the center of the rotor 1132. The rotation shaft 1160 rotates together with the rotor 1132 and transmits the rotational force generated by the driving motor 1130 to a compression unit 1140 (see FIGS. 3 and 4 ), which will be described later. The rotation shaft 1160 is inserted and fixed to the rotor 1132 by shrink fit (or hot press fit).

Meanwhile, an area surrounded by the front end 1110a of the main housing 1110 exists on the rear surface of the inverter cover 1220. The area enclosed by the front end 1110a of the main housing 1110 covers the front opening of the main housing 1110.

A rotation shaft support part 1211 is formed in the center of the area surrounded by the front end 1110a of the main housing 1110. The rotation shaft support part 1211 is for supporting the rotation shaft 1160 in the radial direction.

Here, a direction based on the rotation axis 1160 is defined. The rotation shaft 1160 extends from the front to the rear of the electric compressor 1000, and the direction in which the rotation shaft 1160 extends is defined as an axial direction. In addition, the radial direction of the rotation shaft 1160 is defined as a normal direction toward the main housing 1110 with the shortest distance from an arbitrary point existing on the outer circumferential surface of the rotation shaft 1160. The axial direction and the radial direction are orthogonal to each other.

The rotation shaft support part 1211 protrudes in the axial direction from the rear surface (second surface) of the inverter cover 1220 toward the rotation shaft 1160. The rotation shaft support 1211 is disposed in front of the rotation shaft 1160 in the axial direction. The rotation shaft support 1211 may be formed to surround the front end of the rotation shaft 1160 in a radial direction. A first bearing 1171 is installed inside the rotation shaft support part 1211, and the first bearing 1171 is formed to support the rotation shaft 1160 in a radial direction. The first bearing 1171 may be formed as an annular ball bearing. The first bearing 1171 is not shown in FIG. 2 and is shown in FIGS. 3 and 4.

The rotation shaft 1160 needs to be supported by two points in the radial direction for stable rotation. As described in the above paragraph, the rotation shaft 1160 is supported by one point in the motor chamber S1 by the rotation shaft support part 1211 and the first bearing 1171. The remaining one point is supported by the compression unit 1140. This will be described later.

A rib 1212 is formed around the rotation shaft support 1211. The rib 1212 protrudes from the second surface of the inverter cover 1220. The rib 1212 may be formed in plural. The rib 1212 may protrude along a concentric circle centered on the rotation shaft support part 1211, and may be formed along a straight line connecting the concentric circle in a radial direction. The rib 1212 reinforces the rigidity of the inverter cover 1220 and increases an area in contact with the compression target fluid sucked through the intake port 1111 to increase the cooling effect of the inverter cover 1220.

A three-phase airtight terminal 1230 is exposed on one side of the rotation shaft support 1211. The three-phase airtight terminal 1260 is electrically connected to the driving motor 1130 driven in three phases (UVW), and transmits power and electrical control commands from the inverter module 1200 to the driving motor 1130.

Hereinafter, the internal structure of the electric compressor 1000 will be described in more detail with reference to the drawings and cross-sectional views of the electric compressor 1000 broken down into smaller units than in FIG. 2.

3 is an exploded perspective view of the electric compressor 1000 shown in FIGS. 1 and 2.

4 is a cross-sectional view of the electric compressor 1000 shown in FIGS. 1 and 2.

5 is a perspective view of the fixed scroll 1141 and the orbiting scroll 1142 shown in FIG. 3 viewed from different directions.

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

The compression module 1100 includes a main housing 1110, a rear housing 1120, an electric unit 1130, a compression unit 1140, a main frame 1150, a rotating shaft 1160, and the like.

First, the main housing 1110 will be described.

The main housing 1110 has a shape of a hollow cylinder or a polygonal column. Both the front end 1110a and the rear end 1110b of the main housing 1110 are open. Here, the front end 1110a and the rear end 1110b are defined based on the flow of the fluid to be compressed. For example, the front end 1110a refers to the inverter module 1200 side, and the rear end 1110b refers to the rear housing 1120 side. The front end 1110a may be referred to as a first end, and the rear end 1110b may be referred to as a second end. The inverter module 1200 is coupled to the front end 1110a of the main housing 1110, and the rear housing 1120 is coupled to the rear end 1110b of the main housing 1110.

A sealing member receiving groove is formed in the main housing 1110. The sealing member receiving groove is recessed in a closed curve shape toward the axial direction. The sealing member receiving groove may be formed along a circumference formed at each of the front end 1110a and the rear end 1110b of the main housing 1110.

Sealing members 1115 and 1116 having a closed curve shape such as an O-ring are seated in the sealing member receiving groove. The front sealing member 1115 prevents the fluid to be compressed from leaking through the gap between the main housing 1110 and the inverter cover 1220. The rear sealing member 1116 prevents a fluid to be compressed from leaking through a gap between the main housing 1110 and the rear housing 1120.

The main housing 1110 forms a motor chamber S1 together with the main frame 1150 and the inverter cover 1220. The motor room S1 means a space in which the electric unit 1130 is installed. When the main frame 1150 and the inverter cover 1120 are disposed on both sides of the driving motor 1130, a motor chamber S1 that is distinguished from other spaces is formed. However, since the fluid to be compressed is supplied to the compression unit 1140 through the motor chamber S1, being distinguished from other spaces does not mean that they are completely blocked or isolated from other spaces.

The circumference of the main housing 1110 is formed to surround the electric unit 1130 or to accommodate the electric unit 1130. For example, an irregularity 1115 corresponding to an outer peripheral surface of the permanent magnet forming the stator 1131 may be formed on the inner peripheral surface of the main housing 1110.

The electric unit 1130 is seated in the motor chamber S1 of the main housing 1110. The inverter module 1200 is coupled to the front end of the main housing 1110 for sealing the motor chamber S1, except for the area opened for the flow of the fluid to be compressed, and the main frame is inside the main housing 1110. (1150) is installed.

A plurality of fastening member coupling holes 1114 are formed in the rear end 1110b of the main housing 1110. The fastening member coupling hole 1114 may be formed at a position spaced apart from each other along the circumference of the rear end 1110b of the main housing 1110. It has been previously described that the main housing 1110 and the rear housing 1120 may be coupled to each other by a plurality of fastening members 1123. The plurality of fastening members 1123 are inserted from the rear housing 1120 toward the main housing 1110 and are inserted into the fastening member coupling holes 1114. Accordingly, the main housing 1110 and the rear housing 1120 are bolted to each other.

Next, the rear housing 1120 will be described.

The rear housing 1120 is coupled to the rear end of the main housing 1110. The rear housing 1120 covers the rear end of the main housing 1110. The rear housing 1120 is coupled to the main housing 1110 along a circumference formed at the rear end of the main housing 1110. The rear housing 1120 is disposed to face the fixed scroll 1141 of the compression unit 1140 in the axial direction.

The rear housing 1120 may be understood as a cylinder in which one of the two bottom surfaces is blocked, such a polygonal column, or a shape corresponding thereto. For example, the front end of the rear housing 1120 may be open and the rear end may be closed. In addition, the outer wall corresponding to the side surface of the pillar has a shape substantially corresponding to the outer wall of the main housing 1110.

As shown in FIGS. 3 and 4, the circumference at which the two housings 1110 and 1120 are coupled to each other for the coupling of the main housing 1110 and the rear housing 1120 may protrude along the circumference compared to the adjacent outer circumferential surface. .

Referring to FIG. 4, the rear housing 1120 has a recess portion 1124 in a region surrounded by an outer wall. The recess portion 1124 is spaced apart from the fixed plate portion 1141a of the fixed scroll 1141 in the axial direction. A discharge chamber S2 is formed between the rear housing 1120 and the fixed plate portion 1141a by the recess portion 1124.

The discharge chamber S2 refers to a space in which the fluid compressed at high pressure in the compression unit 1140 is discharged. The discharge chamber S2 is a space formed by the rear housing 1120 and the fixed scroll 1141 and is formed to accommodate the refrigerant discharged from the compression unit 1140. The discharge chamber S2 communicates with the discharge port 1121 described in FIG. 1 above. The fluid compressed at high pressure is discharged to the discharge port 1121 through the discharge chamber S2 and the oil separation chamber S3 to be described later.

The oil separation chamber S3 is formed in the rear housing 1120. The oil separation chamber S3 refers to a space for storing oil separated from the fluid to be compressed. The fluid discharged to the discharge chamber S2 includes not only a fluid to be compressed such as a refrigerant but also oil (lubricating oil) for lubricating the moving components of the electric compressor 1000. An oil separator (not shown) may be installed in the oil separation chamber S3 to separate oil from the fluid to be compressed. The oil separation chamber S3 is formed to store oil separated from the fluid to be compressed by the oil separator.

The oil separation chamber S3 communicates with the discharge chamber S2. Based on the flow of the fluid, a discharge chamber (S2), an oil separation chamber (S3), and a discharge port (1121) are sequentially formed. When the refrigerant and oil are discharged from the compression unit 1140, the refrigerant is discharged to the discharge port 1121, and the oil is separated from the refrigerant by an oil separator (not shown) and stored in the oil separation chamber S3. Oil may be stored in the oil separation chamber S3 and then supplied to the lubricating target through the oil guide passage 1125 to be reused.

The oil guide passages 1125, 1141f, 1142e, and 1160d are formed in all of the rear housing 1120, the fixed scroll 1141, the orbiting scroll 1142, and the rotating shaft 1160. The oil guide passages 1125, 1141f, 1142e, and 1160d are for supplying the oil stored in the oil separation chamber S3 to the object to be lubricated.

The oil guide passage 1125 formed in the rear housing 1120 is formed along the axial direction from the oil separation chamber S3 and is exposed to the front end of the rear housing 1120. Here, the front end of the rear housing 1120 refers to a portion that meets the fixed scroll 1141. A pressure reducing member 1180 is installed in the fixed scroll 1141, and oil is supplied to the pressure reducing member 1180 along the oil guide passage 1125.

A step 1126 is formed along the circumference inside the front end of the rear housing 1120. A fixed scroll 1141 is mounted on the step 1126. The fixed plate portion 1141a of the fixed scroll 1141 is supported in the axial direction and in the radial direction by the step 1126. Due to the high pressure formed in the compression chamber V, the fixed scroll 1141 receives force in the direction toward the rear side of the electric compressor 1000, but the axial position of the fixed scroll 1141 due to the step 1126 Can be fixed.

A sealing member receiving groove is formed in the step 1126. The sealing member receiving groove is formed by being recessed in a direction away from the fixed scroll 1141 along the circumference of the step. A sealing member 1117 such as an O-ring is seated in the sealing member receiving groove. This sealing member 1117 may be understood to be disposed at the boundary between the rear housing 1120 and the fixed scroll 1141.

Since the transmission unit 1130 has been described above, the compression unit 1140 will be described next.

The compression unit 1140 is formed to compress a fluid to be compressed, such as a refrigerant, by a rotational motion. The compression unit 1140 is formed on the rear side of the electric unit 1130 in the axial direction. The compression unit 1140 includes a fixed scroll 1141 and an orbiting scroll 1142. The compression unit 1140 is formed by a fixed scroll 1141 and an orbiting scroll 1142. The fixed scroll 1141 and the orbiting scroll 1142 may be referred to as a first scroll and a second scroll (or vice versa), respectively.

The fixed scroll 1141 and the orbiting scroll 1142 are disposed to face each other in the axial direction. In the axial direction, the fixed scroll 1141 is disposed relatively far from the electric unit 1130, and the orbiting scroll 1142 is disposed relatively close to the electric unit 1130. The fixed scroll 1141 is disposed between the orbiting scroll 1142 and the rear housing 1120 in the axial direction. The orbiting scroll 1142 is disposed between the main frame 1150 and the fixed scroll 1141 in the axial direction.

The fixed scroll 1141 and the orbiting scroll 1142 are coupled to each other to form a pair of compression chambers (V). As the orbiting scroll 1142 rotates with respect to the fixed scroll 1141, the volume of the compression chamber V repeatedly changes, and accordingly, fluid such as a refrigerant is compressed in the compression chamber V.

The fixed scroll 1141 is disposed on one side (rear side) of the driving motor 1130 and is fixed to the inside of the main housing 1110. The outer circumferential surface of the fixed scroll 1141 is in close contact with the inner circumferential surface of the main housing 1110. The fixed scroll 1141 is supported by the main housing 1110 and/or the rear housing 1120 in the radial direction of the rotating shaft 1160. In addition, the fixed scroll 1141 is supported by the rear housing 1120 in the axial direction of the rotation shaft 1160.

The orbiting scroll 1142 is disposed between the drive motor 1130 and the fixed scroll 1141. The orbiting scroll 1142 is connected to the driving motor 1130 by a rotating shaft 1160. The orbiting scroll 1142 is rotated by a rotational force provided from the drive motor 1130.

Hereinafter, a detailed structure of the fixed scroll 1141 will be described.

The fixed scroll 1141 accommodates a fixed plate portion 1141a, a fixed wrap 1141b, a side wall portion 1141c, a fluid suction passage 1141d, a fluid discharge passage 1141e, an oil guide passage 1141f, and a pressure reducing member. It includes a groove 1141g.

The fixed plate portion 1141a is formed in a plate shape. The outer circumferential surface of the fixed plate portion 1141a is formed in a shape corresponding to the inner circumferential surface of the main frame 1150. For example, the fixed plate portion 1141a has a disk shape, and the outer diameter of the fixed plate portion 1141a is substantially the same as the inner diameter of the main housing 1110. Accordingly, the fixed plate portion 1141a may be press-fit into the main housing 1110.

The fixed plate portion 1141a is disposed to face the orbiting plate portion 1142a at a position spaced apart from the orbiting plate portion 1142a of the orbiting scroll 1142. Except for a portion corresponding to the recess portion 1124, the fixed plate portion 1141a may be in close contact with the rear housing 1120. When the fixed plate portion 1141a is in close contact with the rear housing 1120, the discharge chamber S2 is formed by the recess portion 1124 of the rear housing 1120.

If the surface facing the orbiting scroll 1142 among both surfaces of the fixed plate portion 1141a is referred to as the first surface, and the surface facing the rear housing 1120 is referred to as the second surface, the first surface has a fixed wrap 1141b. Is formed, and a sealing member receiving groove (not shown) is formed on the second surface.

The sealing member receiving groove is formed by being recessed in a closed curve shape on the first surface of the fixed plate portion 1141a. The recess direction of the sealing member receiving groove is a direction away from the rear housing 1120. A sealing member 1118 having a closed curved shape such as an O-ring is seated in the sealing member receiving groove. This sealing member 1118 is for preventing leakage of the fluid discharged into the discharge chamber S2.

The fixed wrap 1141b protrudes toward the orbiting scroll 1142 in an involute curve, an arithmetic vortex (Archimedean spiral), or a logarithmic vortex (logarithmic spiral) shape. The involute curve means a curve corresponding to the trajectory drawn by the end of the thread when the thread wound around the base circle having an arbitrary radius is pulled out without loosening. The arithmetic vortex refers to a trace drawn by the moving point when the moving point is away from the reference point at a constant speed along a straight line rotating at a constant angular velocity around a fixed reference point. And the logarithmic eddy line means a curve that follows a constant logarithmic function in polar coordinates. The fixing wrap 1141b may be formed in various shapes in addition to that.

The fixed wrap (1141b) is engaged with the orbiting wrap (1142b) to form a pair of compression chambers (V). The fixed wrap 1141b is inserted between the orbiting wraps 1142b, and the orbiting wrap 1142b is inserted between the fixed wraps 1141b.

The side wall portion 1141c protrudes in an annular shape toward the orbiting scroll 1142 along the outer rim of the fixed plate portion 1141a. The side wall portion 1141c is formed to surround the fixing wrap 1141b in the radial direction of the rotation shaft 1160.

The outer circumferential surface of the side wall portion 1141c is in close contact with the inner circumferential surface of the main housing 1110. Accordingly, the fixed scroll 1141 may be fixed inside the main housing 1110 in the radial direction of the rotation shaft 1160.

The protruding end (front end) of the side wall portion 1141c may be in surface contact with the main frame 1150. The main frame 1150 includes a back pressure chamber side wall portion 1150d corresponding to the orbiting scroll 1142, and an end portion of the side wall portion 1141c is in close contact with the back pressure chamber side wall portion 1150d. As the annular side wall portion 1141c is in close contact with the back pressure chamber side wall portion 1150d of the main frame 1150, a seating space for the orbiting scroll 1142 is formed between the fixed scroll 1141 and the main frame 1150.

An annular thrust plate (not shown) may be additionally installed between the side wall portion 1141c and the back pressure chamber side wall portion 1150d in the axial direction of the rotation shaft 1160. The thrust plate may be fixed by the side wall portion 1141c and the main frame 1150.

The fluid suction passage 1141d may be formed inside the side wall portion 1141c. The fluid suction passage 1141d is opened toward the axial direction and/or the radial direction of the rotation shaft 1160. The fluid suction passage 1141d communicates with the motor chamber S1 and the compression chamber V. The fluid to be compressed is introduced into the compression chamber V from the motor chamber S1 through the fluid suction passage 1141d, and is compressed by the compression unit 1140 in the compression chamber V.

The fluid discharge passage 1141e penetrates the fixed plate portion 1141a in the axial direction of the rotation shaft 1160 to discharge the fluid compressed in the compression chamber V. The fluid discharge passage 1141e communicates with the compression chamber V and the discharge chamber S2. The fluid compressed in the compression chamber V is discharged to the discharge chamber S2 through the fluid discharge passage 1141e.

A discharge valve 1143 for opening and closing the fluid discharge passage 1141e may be installed in the fixed plate portion 1141a. The discharge valve 1143 is formed to open passively above the reference pressure and close passively below the reference pressure. As compression of the refrigerant to be compressed in the compression unit 1140 is performed, when the pressure in the compression chamber V exceeds the preset pressure, the discharge valve 1143 is opened.

The oil guide passage 1141f is formed in the fixed plate portion 1141a, or is formed in the fixed plate portion 1141a and the side wall portion 1141c. The oil guide passage 1141f is formed to receive oil from the oil separation chamber S3 through the pressure reducing member 1180 and guide the supplied oil to a lubrication target.

For example, the oil guide passage 1141f penetrates the fixed plate portion 1141a in the radial direction by a length corresponding to the radius of the fixed plate portion 1141a. In addition, the oil guide passage 1141f again penetrates the fixed plate portion 1141f in the axial direction by a length equal to half the thickness of the fixed plate portion 1141a.

For example, the inlet of the oil guide flow path 1141f is formed at a position facing the pressure reducing member 1180, the oil guide flow path 1141f passes through the fixed scroll 1141, and the outlet of the oil guide flow path 1141f is pivoted. It is formed in a position facing the cover portion 1142d of the scroll 1142. The oil is guided from the oil separation chamber S3 to the lid 1142d by the oil guide passage 1141f.

A pressure-sensitive member receiving groove 1141g is formed in a position where the rear housing 1120 and the fixed plate portion 1141a are in contact with each other and face each other. The pressure reducing member receiving groove 1141g may be formed by being recessed from the rear surface of the fixed plate portion 1141, and the recess direction is a direction away from the rear housing 1120 along the axial direction. A decompression member 1180 for depressurizing the oil of the discharge pressure to an intermediate pressure is inserted into the decompression member receiving groove 1141g. Alternatively, the pressure-reducing member receiving groove 1141g may be formed in the rear housing 1120.

The decompression member 1180 is formed to depressurize the oil supplied from the oil separation chamber S3. The oil of the discharge pressure stored in the oil separation chamber S3 is reduced to an intermediate pressure by the pressure reducing member 1180. The intermediate pressure refers to a pressure higher than the suction pressure corresponding to the pressure before compression of the fluid and lower than the discharge pressure corresponding to the pressure after compression of the fluid. An orifice or the like may be used as the pressure reducing member 1180.

The orbiting scroll 1142 is seated on the thrust portion 1150c of the main frame 1150. If the electric compressor 1000 has a thrust plate, the orbiting scroll 1142 is seated on the thrust plate. The orbiting scroll 1142 is supported by the main frame 1150 or thrust plate in the axial direction. The orbiting scroll 1142 forms a compression chamber V together with the fixed scroll 1141. The orbiting scroll 1142 is formed to compress a fluid by orbiting with respect to the fixed scroll 1141.

The orbiting scroll 1142 includes an orbiting plate portion 1142a, an orbiting wrap 1142b, a rotating shaft coupling portion 1142c, a cover portion 1142d, and an oil guide passage 1142e.

The turning plate portion 1142a is formed in a plate shape corresponding to the fixed plate portion 1141a. Since the orbiting plate portion 1142a needs to rotate within the area enclosed by the main housing 1110, the outer diameter of the orbiting plate portion 1142a is formed smaller than the inner diameter of the main housing 1110.

The orbiting plate portion 1142a may have an outer diameter smaller than that of the sidewall portion 1141c of the fixed scroll 1141. Accordingly, the orbiting plate portion 1142a may be seated on the fixed wrap 1141b of the fixed scroll 1141 in the axial direction. When the turning plate portion 1142a is seated on the fixed wrap 1141b, the turning plate portion 1142a and the fixed wrap 1141b may form a thrust surface.

When the side facing the main frame 1150 of both sides of the turning plate portion 1142a is referred to as the first side (front), and the side facing the fixed scroll 1141 is referred to as the second side (rear side), the first A groove is formed on the surface, and a rotation shaft coupling portion 1142c and a revolving wrap 1142b are formed on the second surface. Here, the groove formed on the first surface corresponds to the opening of the rotation shaft coupling portion 1142c.

Since the turning plate portion 1142a is supported by the main frame 1150 in the axial direction of the rotation shaft, the thrust surface corresponding to the thrust portion 1150c of the main frame 1150 is also applied to the first surface of the turning plate portion 1142a. To form.

An annular thrust plate (not shown) described above may be installed between the turning hard plate portion 1142a and the main frame 1150. If the electric compressor 1000 has a thrust plate, the orbiting scroll 1142 is seated on the thrust plate. The orbiting scroll 1142 is supported by the main frame 1150 or thrust plate in the axial direction.

The orbiting wrap 1142b protrudes toward the fixed scroll 1141 from the second surface of the orbiting plate portion 1142a. Like the fixed wrap 1141b, the orbiting wrap 1142b may have an involute curve, an arithmetic vortex (Archimedean spiral), or a logarithmic vortex (logarithmic spiral) shape. The orbiting wrap 1142b may be formed in a variety of other shapes.

The orbiting wrap 1142b may be in close contact with the fixed plate portion 1141a in the axial direction. Likewise, the fixing wrap 1141b may also be in close contact with the turning hard plate portion 1142a in the axial direction. A tip chamber (not shown) is installed at at least one of an axial end of the fixed wrap 1141b and an axial end of the orbiting wrap 1142b to seal the compression chamber V.

The rotation shaft coupling portion 1142c protrudes in the axial direction along a circle from the second surface of the turning plate portion 1142a. The rotation shaft coupling portion 1142c is formed to surround the eccentric portion 1160c of the rotation shaft 1160 in the radial direction of the rotation shaft 1160. The rotation shaft coupling portion 1142c is formed at the innermost part of the vortex defining the shape of the orbiting wrap 1142b.

The rotation shaft coupling portion 1142c may be understood to correspond to a side surface of a hollow cylinder. The first end (front end) of the rotation shaft 1160 passes through the drive motor 1130, and the second end (rear end) is inserted into the orbiting scroll 1142. An eccentric portion 1160c is formed at the second end of the rotation shaft 1160. The eccentric portion 1160c is inserted into the rotation shaft coupling portion 1142c.

The cover portion 1142d is disposed between the eccentric portion 1160c of the rotating shaft 1160 and the fixed plate portion 1141a of the fixed scroll 1141 so as to cover the eccentric portion 1160c in the axial direction. The cover portion 1142d is coupled to the rotation shaft coupling portion 1142c along the circumference of the cover portion 1142d. If the rotation shaft coupling portion 1142c is a hollow cylinder shape, the cover portion 1142d may be understood to correspond to one of the two bottom surfaces of the cylinder. The cover portion 1142d may be formed at a position farthest from the orbiting plate portion 1142a in the axial direction of the rotation shaft 1160.

Assuming that the rotation shaft coupling portion 1142c forms the side surface of the cylinder and the cover portion 1142d forms one bottom surface of the cylinder, the other bottom surface is opened for insertion of the rotation shaft. Except for the opened area and the oil guide passage 1142e to be described later, the rotation shaft coupling portion 1142c and the cover portion 1142d form a closed structure around the eccentric portion 1160c.

The closed structure conceptually refers to a structure in which the flow of the fluid to be compressed existing in the compression chamber V is blocked so that no reverse flow occurs. Therefore, the closed structure around the eccentric portion 1160c corresponds to a structure in which the fluid in the compression chamber V or the discharge chamber S2 does not flow back to the eccentric portion 1160c. If the rotating shaft 1160 completely penetrates the orbiting scroll 1142, since there is no cover part 1142d, a high-pressure fluid flows back between the rotating shaft coupling part 1142c and the rotating shaft 1160.

According to the closed structure shown in FIG. 4, the high-pressure fluid does not flow back. The reason why the closed structure can be introduced around the eccentric part 1160c in this way is possible because the rotation shaft 1160 is supported by the compression part 1140 and the transmission part by one point. Here, the direction in which the rotation shaft 1160 is supported indicates the radial direction of the rotation shaft 1160. In addition, the second bearing 1172 inserted into the main frame 1150 supports the rotation shaft 1160 in the compression unit 1140.

The second bearing 1172 is formed to surround the rotation shaft 1160 in the radial direction of the rotation shaft 1160. For example, the second bearing 1172 may be formed of a hollow cylindrical bush bearing. The second bearing 1172 is inserted into the rotation shaft receiving portion 1150a of the main frame 1150.

Unlike the present invention, if the rotary shaft 1160 is supported only by two points in the compression unit 1140, the two supporting points will be the second bearing 1172 and the fixed scroll 1141. In this case, the rotating shaft 1160 completely penetrates the orbiting scroll 1142, is inserted into the fixed scroll 1141, and is supported by the second bearing 1172 and the fixed scroll 1141 by one point. In this way, the positions of the two points supporting the rotation shaft 1160 in the radial direction are all concentrated on the compression unit 1140. In this way, if the rotation shaft 1160 is supported only by two points in the compression part 1140, the rotation shaft 1160 essentially penetrates the orbiting scroll 1142, and the cover portion 1142d cannot be formed on the orbiting scroll 1142. .

Assuming that a structure in which several fluid discharge passages including a bypass passage are formed in the fixed scroll 1141 is referred to as A structure, and a structure in which only one fluid discharge passage is formed without a bypass passage is arbitrarily assumed to be a B structure, a rotating scroll ( As the cover portion 1142d is introduced in 1142), the structure A can be replaced with the structure B. The present invention corresponds to the B structure.

If the size of the fluid discharge passage 1141e formed in the fixed scroll 1141 of the present invention is compared 1:1 with the bypass passage or the fluid discharge passage formed in the structure A, the fluid discharge passage 1141e of the present invention is Have a larger size. Therefore, when the problem of insufficient discharge area of the fluid to be compressed cannot be solved by increasing the number of bypass flow paths, such as an electric compressor operated at a high compression ratio, when the structure of the present invention is introduced, only one fluid discharge flow path 1141e is required to be compressed. It is possible to sufficiently secure the discharge area of the fluid, and the problem of lowering the indication efficiency can also be solved.

In particular, according to the present invention corresponding to the structure B, the number of discharge valves 1143 to be provided as many as the number of bypass flow paths or fluid discharge flow paths 1141e can be reduced to one. The reduction in the number of discharge valves 1143 has effects such as simplification of the structure of the electric compressor 1000, reduction of possible failure factors, reduction of manufacturing cost, and the like.

The oil guide passage 1142e is formed in the cover portion 1142d. The oil guide passage 1142e may pass through the cover portion 1142d along the axial direction of the rotation shaft 1160. While the oil guide flow path 1141f of the fixed scroll 1141 is fixed, the oil guide flow path 1142e of the orbiting scroll 1142 is not fixed because the orbiting scroll 1142 pivots with respect to the fixed scroll 1141. Does not.

However, in order to supply oil smoothly, the oil guide flow path 1141f of the fixed scroll 1141 and the oil guide flow path 1142e of the orbiting scroll 1142 must be temporarily overlapped within the orbiting motion range of the orbiting scroll 1142. If possible, it is desirable to continue overlapping. Here, the direction in which the oil guide flow path 1141f of the fixed scroll 1141 and the oil guide flow path 1142e of the orbiting scroll 1142 overlap each other is the axial direction of the rotation shaft 1160.

As the oil guide flow path 1142e is formed in the orbiting scroll 1142, the oil supplied through the oil guide flow path 1141f of the fixed scroll 1141 is rotated through the oil guide flow path 1142e of the orbiting scroll 1142. It is supplied to the eccentric portion 1160c of the 1160.

An anti-rotation mechanism (not shown) may be installed on the orbiting scroll 1142.

The anti-rotation mechanism is formed to prevent rotation of the orbiting scroll 1142 and to rotate the orbiting scroll 1142. If there is no anti-rotation mechanism, the orbiting scroll 1142 will rotate by the rotational force transmitted through the rotational shaft 1160 or the like. When the orbiting scroll 1142 rotates, the fluid cannot be compressed, and the orbiting scroll 1142 must rotate with respect to the fixed scroll 1141 to compress the fluid.

As a type of anti-rotation mechanism, a pin and ring may be applied, or an Oldham ring may be applied. In addition, various devices can be applied as anti-rotation devices. The anti-rotation mechanism may be disposed between the orbiting scroll 1142 and the main frame 1150.

Next, the main frame 1150 will be described.

The main frame 1150 is formed to support the orbiting scroll 1142 in the axial direction of the rotation shaft 1160 so as to be capable of orbiting. The main frame 1150 is disposed on the opposite side of the fixed scroll 1141 around the orbiting scroll 1142 to form a back pressure chamber S4 together with the orbiting scroll 1142.

An unevenness 1115 (or step) is formed along the circumference of the inner circumferential surface of the main housing 1110. When the inner diameter of the portion where the unevenness 1115 is formed and the inner diameter of the rear side are compared with each other, the rear inner diameter is larger. Accordingly, the main frame 1150 may be seated on the irregularities 1115 in the axial direction.

The main frame 1150 includes a rotating shaft receiving portion 1150a, a main plate portion 1150b, a thrust portion 1150c, and a back pressure chamber side wall portion 1150d.

The rotation shaft receiving portion 1150a is formed to surround the rotation shaft 1160 penetrating the main frame 1150. The length of the rotation shaft receiving portion 1150a in the axial direction of the rotation shaft 1160 is longer than the length of the main hard plate portion 1150b, which will be described later.

The second bearing 1172 is inserted in the area surrounded by the rotation shaft receiving part 1150a. As described above, the second bearing 1172 is formed to surround the rotation shaft 1160 in the radial direction of the rotation shaft 1160. It has been previously described that the second bearing 1172 may be formed of a hollow cylindrical bush bearing.

The main hard plate portion 1150b is formed in an annular shape around the rotation shaft receiving portion 1150a. The rotation shaft receiving portion 1150a described above is formed inside the annular shape. The main hard plate 1150b is disposed at a position facing the orbiting hard plate 1142a of the orbiting scroll 1142 in the axial direction. The main hard plate portion 1150 corresponds to a portion that is seated on the irregularities 1115 of the main housing 1110.

The thrust portion 1150c partially contacts the orbiting plate portion 1142a of the orbiting scroll 1142 to form a thrust surface. In order to form a thrust surface, the thrust portion 1150c may protrude from the main hard plate portion 1150b toward the orbiting scroll 1142. Accordingly, the thrust portion 1150c supports the orbiting scroll 1142 in the axial direction.

The back pressure chamber sidewall portion 1150d is formed to surround the rotation shaft 1160 at a position spaced apart from the rotation shaft 1160 based on the radial direction. The back pressure chamber side wall portion 1150d protrudes in an annular shape along the axial direction of the rotation shaft 1160 around the main plate portion 1150b to form a side wall of the back pressure chamber S4. The back pressure chamber side wall portion 1150c may abut the side wall portion 1141c of the fixed scroll 1141 along the circumference.

The back pressure chamber S4 is formed between the orbiting scroll 1142 and the main frame 1150. The back pressure chamber S4 is a space for preventing a phenomenon that a high pressure is formed in the compression chamber V and the orbiting scroll 1142 is pushed. The pressure in the back pressure chamber S4 is a pressure smaller than the discharge pressure in the compression chamber V.

The back pressure chamber (S4) is isolated from the flow path through which the fluid is sucked into the compression chamber (V). In order to isolate and seal the back pressure chamber S4, an annular sealing member (not shown) is provided between the thrust portion 1150c and the swing plate portion 1142a.

Next, the rotation shaft 1160 will be described.

The rotation shaft 1160 is connected to the rotor 1132 and the orbiting scroll 1142 to transmit the rotational force provided from the drive motor 1130 to the orbiting scroll 1142.

The rotation shaft 1160 has a first end (front end) and a second end (rear end). The first stage is located on the opposite side of the orbiting scroll 1142 with respect to the drive motor 1130 in the axial direction of the rotation shaft 1160. The second stage is located between the main frame 1150 and the fixed scroll 1141 in the axial direction of the rotating shaft 1160.

The first end of the rotating shaft 1160 is supported in the radial direction by the rotating shaft support 1211 and the first bearing 1171. An eccentric portion 1160c is formed at the second end of the rotation shaft 1160. A portion between the first end and the second end of the rotation shaft 1160 passes through the rotor 1132 and the main frame 1150.

When describing the structure of the rotation shaft along the axial direction from the first end of the rotation shaft 1160 to the second end, a portion inserted into the rotor 1132 of the drive motor 1130 between the first end and the second end ( 1160a), a portion 1160b inserted into the rotation shaft receiving portion 1150a of the main frame 1150 is formed. Any part is formed in a cylindrical shape. Since the part 1160b inserted into the rotation shaft receiving part 1150a of the main frame 1150 forms a bearing surface with the second bearing 1172, the part may be referred to as a bearing part 1160b.

All of the remaining portions 1160a and 1160b of the rotation shaft excluding the eccentric portion 1160c are centered in the axial direction of the rotation shaft 1160. On the other hand, the center of the eccentric part 1160c is eccentric from the center of the rotation shaft 1160. Therefore, when the eccentric portion 1160c is inserted into the orbiting scroll 1142, the orbiting scroll 1142 is eccentrically coupled to the rotation shaft 1160.

The bearing portion 1160b is supported by the second bearing 1172 between the driving motor 1130 and the eccentric portion 1160c. Here, the second bearing 1172 supports the bearing part 1160b in the radial direction of the rotation shaft 1160.

The oil guide flow path 1160d of the rotation shaft 1160 may pass through the eccentric part 1160c along the axial direction, and may additionally pass through the bearing part 1160b. In addition, an oil supply port 1160e opened in the radial direction in the oil guide passage 1160d is formed. The oil supply port 1160e may be exposed on the outer peripheral surface of the eccentric portion 1160c.

The oil guide flow path 1160d of the rotation shaft 1160 is formed at a position facing the oil guide flow path 1142e of the orbiting scroll 1142 in the axial direction. Accordingly, when oil is supplied to the oil guide flow path 1160d of the rotation shaft 1160 through the oil guide flow path 1142e of the orbiting scroll 1142, the oil is again supplied with the oil guide flow path 1160d of the rotation shaft 1160. It is supplied to the outer peripheral surface of the eccentric portion 1160c through the port 1160e. Since the eccentric portion 1160c is coupled with the rotation shaft coupling portion 1142c of the orbiting scroll 1142, the oil lubricates the outer peripheral surface of the eccentric portion 1160c and the inner peripheral surface of the rotation shaft coupling portion 1142c.

In addition, the space between the outer circumferential surface of the eccentric portion 1160c and the inner circumferential surface of the rotation shaft coupling portion 1142c communicates with the back pressure chamber S4. Accordingly, the oil discharged from the oil supply port 1160e is supplied to the back pressure chamber S4 to form a back pressure for the compression chamber V.

Next, the balance weight 1161 will be described.

The balance weight 1161 is coupled to the rotation shaft between the drive motors 1130 and 1130 and the bearing part. The balance weight 1161 is installed to offset an eccentric load (or eccentric amount) of the rotation shaft 1160. The balance weight 1161 includes a first portion 1161a and a second portion 1161b.

The first part 1161a is formed in an annular shape to surround the rotation shaft 1160. Assuming that the first portion 1161a is a disk, the diameter of the first portion 1161a is larger than the diameter of the rotation shaft 1160.

The second part 1161b first extends from the rim of the first part 1161a toward the axial direction of the rotation shaft 1160 or a radial direction inclined thereto, and extends secondly toward the radial direction of the rotation shaft 1160. . The primary extension of the second portion 1161b does not extend from all 360° around the first portion 1161a, but extends from a circular arc having a constant central angle. Accordingly, the second extending portion may have a shape of an annular sector. The second portion 1161b surrounds the rotation shaft 1160 only in a range corresponding to the central angle.

The balance weight 1161 does not necessarily have to be installed if there is one, nor does it need to be coupled only to the rotation shaft 1160. For example, a balance weight 1162 may also be installed on the rotor 1132 (see FIG. 4). An ordinal number such as the first balance weight 1161 and the second balance weight 1162 may be added to distinguish the two balance weights 1161 and 1162. Any purpose for offsetting the eccentric load (or eccentric amount) of the rotating object is the same.

Finally, an annular sealing member 1119 may be installed between the rotation shaft support 1211 and the inverter cover 1220 (see FIG. 4 ). The sealing member 1119 prevents the fluid to be compressed from penetrating into the inverter module 1200 through the space between the rotation shaft support 1211 and the inverter cover 1220.

Next, the fluid discharge passage 1141e formed in the fixed scroll 1141 will be described with reference to FIGS. 6 and 7.

6 is a cross-sectional view showing a compression chamber V formed by the fixed scroll 1141 and the orbiting scroll 1142. The position of the cross section corresponds to A-A shown in FIG. 4.

The fluid discharge passage 1141e of the fixed scroll 1141 is formed at a position overlapping with the rotation shaft coupling portion 1142c and/or the cover portion 1142d of the orbiting scroll 1142 in the axial direction of the rotation shaft 1160. The fact that the fluid discharge passage 1141e of the fixed scroll 1141 overlaps the rotation shaft coupling portion 1142c and/or the cover portion 1142d of the orbiting scroll 1142 indicates that the size of the fluid discharge passage 1141e is sufficiently large. it means. Since the cover portion 1142d is formed on the orbiting scroll 1142, the fluid discharge passage 1141e of the fixed scroll 1141 overlaps with the rotational shaft coupling portion 1142c and/or the cover portion 1142d of the orbiting scroll 1142 Even if it does, backflow of the fluid to be compressed does not occur.

Here, the fluid discharge passage 1141e of the fixed scroll 1141 and the rotation shaft coupling part 1142c and/or the cover part 1142d of the orbiting scroll 1142 do not completely overlap in the axial direction of the rotation axis, but partially overlap. do. If the fluid discharge passage 1141e of the fixed scroll 1141 and the rotation shaft coupling portion 1142c and/or the cover portion 1142d of the orbiting scroll 1142 completely overlap, the rotation shaft coupling portion 1142c and/or the cover portion 1142d ) Blocks the fluid discharge passage 1141e.

The fixed wrap 1141b is formed along the vortex, and the fluid discharge passage 1141e of the fixed scroll 1141 is between the center of the fixed swash plate 1141a and the innermost part P of the vortex 1141a. ) Through. More specifically, when the center of the fixed plate portion 1141a is referred to as a first point (I) and the innermost portion (P) of the vortex is referred to as a second point (II), the fluid discharge passage 1141e is a first point. It is formed in an imaginary circle centered on (I) and has a radius from the first point (I) to the second point (II).

This position where the fluid discharge passage 1141e is formed corresponds to a position communicating with both the pair of compression chambers V formed by the fixed scroll 1141 and the orbiting scroll 1142. When the orbiting scroll 1142 is rotated with respect to the fixed scroll 1141, the increase or decrease of the area where the cover portion 1142d and the fluid discharge passage 1141e overlap is repeated, and the fluid compressed in the compression chamber V is Through this process, it is discharged to the discharge chamber S2.

Meanwhile, when the orbiting scroll 1142 performs orbiting movement, the oil guide flow path 1142e of the orbiting scroll 1142 is also naturally orbited. If the trajectory of the orbiting motion drawn by the oil guide flow path 1142e formed in the orbiting scroll 1142 overlaps the oil guide flow path 1141f of the fixed scroll 1141, the oil guide flow path 1142e of the orbiting scroll 1142 and The oil guide flow path 1141f of the fixed scroll 1141 maintains an overlapping state in the axial direction of the rotation shaft 1160.

The fluid discharge passage 1141e of the fixed scroll 1141 is formed in a position not overlapping with the oil guide passage 1142e of the orbiting scroll 1142 in the axial direction of the rotation shaft 1160. This is because if the fluid discharge passage 1141e overlaps the oil guide passage 1142e, the fluid to be discharged to the fluid discharge passage 1141e may flow back to the oil guide passage 1142e.

7 is a conceptual diagram showing a process of orbiting the orbiting scroll 1142 with respect to the fixed scroll 1141.

Referring to FIG. 7, while the orbiting scroll 1142 is rotating, the cover portion 1142d and the fluid discharge passage 1141e partially overlap each other in the axial direction of the rotation shaft 1160, while the cover portion 1142d. The overlapping area of the fluid discharge passage 1141e increases and decreases repeatedly. Through this process, the opening degree of the fluid discharge passage 1141e is changed. While the overlapping area increases, the compression target fluid is compressed in the compression chamber V, and while the overlapping area decreases, the compression target fluid is discharged from the compression chamber V through the fluid discharge passage 1141e.

Referring to FIG. 7, while the orbiting scroll 1142 rotates, the cover portion 1142d and the fluid discharge passage 1141e partially overlap in the axial direction of the rotation shaft 1160. In addition, while the orbiting scroll 1142 rotates, the rotation shaft coupling portion 1142c and the fluid discharge passage 1141e also maintain a partially overlapped state in the axial direction of the rotation axis. This means that the fluid discharge passage 1141e is sufficiently large, and it means that only one fluid discharge passage 1141e is sufficient to replace the plurality of fluid discharge passages 1141e formed in the compressor of the prior art.

7(f) is a diagram corresponding to the start point of discharge of the compressed fluid in the compression chamber. When the fluid compressed in the first compression chamber V1 and the second compression chamber V2 starts to be discharged, the fluid discharge flow path 1141e is connected to the first compression chamber V1 and the second compression chamber in the axial direction of the rotation shaft 1160. All are superimposed on the compression chamber V2. Accordingly, the fluid compressed in the first compression chamber V1 and the fluid compressed in the second compression chamber V2 are simultaneously discharged.

As described above, the fluid discharge passage 1141e is preferably formed at a position in which the fluid compressed in the first compression chamber V1 and the fluid compressed in the second compression chamber V2 can be simultaneously discharged. If the fluid discharge passage 1141e is biased toward only one of the first compression chamber V1 and the second compression chamber V2, the fluid compressed in one of the two compression chambers V1 and V2 is This is because, while the fluid is smoothly discharged through the fluid discharge passage 1141e, the fluid compressed in the other compression chamber is not smoothly discharged through the fluid discharge passage 1141e. A preferred position of the fluid discharge passage 1141e has been described with reference to FIG. 6 above.

According to the structure provided by the present invention, since a sufficient discharge port area is secured with only one fluid discharge passage 1141e, the problem of insufficient discharge port area and decrease in instruction efficiency can be solved without relying on an increase in the number of bypass passages. Therefore, the compressor of the present invention is a structure suitable for an electric compressor operated at a high compression ratio.

The compression ratio is a comparison of the suction pressure and the discharge pressure of the fluid to be compressed. In particular, the rated operation compression ratio refers to a compression ratio that operates with the highest frequency within the range of the operation compression ratio of the electric compressor 1000. The high compression ratio in the present invention means a rated operating compression ratio of 4 or more, and preferably means a rated operating compression ratio of 5 or more. For example, the structure of the present invention is suitable to be applied to an electric compressor operated with a rated operation compression ratio of 4 or more, preferably a rated operation compression ratio of 5 or more.

The difference in the rated operating compression ratio can result from the refrigerant used in the electric compressor. When a high-pressure refrigerant is used in an electric compressor, the electric compressor is operated at a rated operating compression ratio of low pressure. Conversely, when a low-pressure refrigerant is used in an electric compressor, the electric compressor is operated with a high-pressure rated operation compression ratio.

If the problem of the discharge port area does not occur even with only one fluid discharge passage 1141e in the fixed scroll 1141, it is possible to improve the manufactureability of the compressor. This is because the process for forming the bypass flow path may be omitted. Furthermore, if the fluid is discharged with only one fluid discharge passage 1141e, the fluid may be discharged with an accurate desired discharge pressure.

In addition, according to the present invention, since a closed structure is introduced around the eccentric portion 1160c by the cover portion 1142d and the rotating shaft coupling portion 1142c, the fluid to be compressed is coupled to the rotating shaft even if the size of the fluid discharge passage 1141e is increased. The phenomenon of backflow between the part 1142c and the rotation shaft may be prevented.

Further, according to the present invention, since the oil guide flow path of the cover portion 1142d is formed at a position not overlapping with the fluid discharge flow path 1141e of the fixed scroll 1141, the oil can be supplied to the lubrication target region without backflow of the fluid to be compressed I can.

The electric compressor described above is not limited to the configuration and method of the above-described embodiments, and the embodiments may be configured by selectively combining all or part of each of the embodiments so that various modifications can be made.

Claims (12)

A drive motor having a stator and a rotor;
A fixed scroll fixed to one side of the drive motor;
An orbiting scroll disposed between the driving motor and the fixed scroll to form the fixed scroll and a compression chamber, and for orbiting motion by a rotational force provided from the drive motor; And
It has an eccentric portion formed to be eccentrically coupled to the orbiting scroll, is connected to the rotor and the orbiting scroll to transmit rotational force provided from the drive motor to the orbiting scroll, and an oil guide flow path along the axial direction at the end of the eccentric portion Is formed, the oil guide flow path includes a rotation shaft connected to the oil supply port penetrating through the outer circumferential surface of the eccentric portion,
The orbiting scroll,
Turning hard plate;
An orbiting wrap protruding from the orbiting plate portion toward the fixed scroll along a vortex;
A rotation shaft coupling portion formed at an innermost portion of the orbiting wrap so as to surround the eccentric portion in the radial direction of the rotation shaft; And
It is coupled to the rotation shaft coupling part along a circumference, is disposed between the eccentric part and the fixed scroll so as to cover the eccentric part in the axial direction of the rotation shaft, and at a position furthest from the orbiting plate part in the axial direction of the rotation shaft. It is formed and includes a cover portion in which an oil guide flow path penetrating in the axial direction of the rotation shaft is formed,
In the fixed scroll, a fluid discharge passage is formed at a position that penetrates the fixed scroll in the axial direction of the rotation shaft and partially overlaps with the cover part based on the axial direction of the rotation shaft,
The fluid discharge passage is formed at a position overlapping the cover portion in the axial direction of the rotation shaft,
An oil guide flow path is formed in the cover part at a position facing the oil guide flow path of the rotation shaft in the axial direction,
An oil guide flow path is formed in the fixed scroll at a position facing the oil guide flow path of the cover part in the axial direction,
The oil guide passage formed on the cover portion is formed at a position that does not overlap with each other in the axial direction of the fluid discharge passage and the rotation shaft formed in the fixed scroll. The method of claim 1,
The rotating shaft has a first end and a second end,
The first stage is disposed on the opposite side of the orbiting scroll based on the driving motor,
The first end is supported in the radial direction of the rotation shaft by a first bearing surrounding the rotation shaft,
The eccentric portion is formed in the second end,
The rotating shaft is supported in a radial direction of the rotating shaft by a second bearing surrounding the rotating shaft between the eccentric portion and the driving motor. The method of claim 1,
The electric compressor further includes a main housing having a hollow column shape,
The fixed scroll,
A fixed plate part fixed to the inner circumferential surface of the main housing along the circumference; And
It includes a fixed wrap protruding toward the orbiting scroll from the fixed plate portion along the vortex,
The fluid discharge passage is an electric compressor passing through the fixed plate part between the center of the fixed plate part and the innermost part of the vortex. The method of claim 3,
When the center of the fixed plate portion is referred to as a first point, and the innermost portion of the vortex is referred to as a second point, the fluid discharge passage is centered on the first point and extends from the first point to the second point. An electric compressor formed in an imaginary circle with a radius. delete delete The method of claim 1,
While the orbiting scroll maintains an overlapping state of the cover part and the fluid discharge flow path while the orbiting scroll rotates, the overlapping area between the cover part and the fluid discharge flow path increases and decreases repeatedly. delete delete The method of claim 1,
The electric compressor has a rated operation compression ratio of 5 or more. The method of claim 1,
An electric compressor in which a step or inclination is formed in at least one of the fixed scroll and the orbiting scroll so that the cover part and the fluid discharge passage are spaced apart from each other. delete

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