KR102454722B1 - Hermetic compressor - Google Patents

Abstract

The hermetic compressor according to this embodiment includes a refrigerant discharge pipe passing through a casing and communicating with the inner space of the casing, wherein the refrigerant discharge pipe is at least one or more on the main surface of the inner accommodating part belonging to the inner space of the casing A discharge passage may be formed. Through this, as a part of the refrigerant passes through the narrow discharge passage and flows into the refrigerant discharge pipe, the oil separation effect may be improved by receiving flow resistance to the refrigerant.

Description

Hermetic compressor {HERMETIC COMPRESSOR}

FIELD OF THE INVENTION The present invention relates to compressors, and more particularly to hermetic compressors.

In the hermetic compressor, a driving motor constituting an electric part and a compression unit are installed together in the inner space of the casing. .

The former is a compressor in which suction refrigerant is filled in the inner space of the casing to form a suction pressure, and the latter is a compressor in which the discharge refrigerant is filled in the inner space of the casing to form a discharge pressure. Hereinafter, the inner space of the casing may be defined as a space in which a driving motor is installed unless otherwise specified.

In the low-pressure compressor, the inner space of the casing is divided into a low-pressure part and a high-pressure part, and a refrigerant suction pipe communicates with the low-pressure part where the driving motor is installed, and the refrigerant discharge pipe communicates with the high-pressure part. Accordingly, in the low-pressure compressor, the low-pressure part acts as a kind of accumulator, and liquid refrigerant or oil can be separated from the gas refrigerant while the refrigerant sucked into the inner space of the casing through the refrigerant suction pipe passes through the low-pressure part.

In the high-pressure compressor, the refrigerant suction pipe is not communicated with the inner space of the casing, but directly communicates with the suction side of the compression chamber. can be communicated directly to Accordingly, in the high-pressure compressor, the refrigerant discharged from the compression unit passes through the inner space of the casing, and then is discharged toward the condenser of the refrigerating cycle through the refrigerant discharge pipe. At this time, the refrigerant is discharged from the compression unit in a state where oil is mixed, but the oil is separated from the refrigerant as the refrigerant passes through the inner space of the casing.

However, the refrigerant discharged from the compression unit does not circulate widely in the inner space of the casing and moves rapidly toward the refrigerant discharge pipe, which in turn causes the oil to flow out into the refrigeration cycle through the refrigerant discharge pipe in a state where it cannot be separated from the refrigerant. . This causes friction loss due to insufficient oil in the compressor.

Patent Document 1 (Korean Patent Publication No. 10-2009-0013042) discloses an example in which a separate oil separator is installed outside a casing in a high-pressure compressor. The oil separator in Patent Document 1 is installed in the middle of the refrigerant discharge pipe communicating with the inner space of the casing.

Accordingly, a part of the refrigerant discharged from the compression unit into the inner space of the casing flows into the oil separator connected to the refrigerant discharge pipe from the outside of the casing, and the gas refrigerant and oil (liquid refrigerant) are separated in the oil separator, and the gas refrigerant is transferred to the refrigerant pipe. While moving to the condenser through the gas refrigerant, the oil separated from the gas refrigerant is returned to the oil pump through the oil return pipe to suppress oil discharge. However, in Patent Document 1, as a separate oil separator is further provided on the outside of the casing, the number of parts increases, thereby increasing the manufacturing cost.

Patent Document 2 (Korean Patent Registration No. 10-0686747) discloses an example in which an oil cap is provided inside a casing in a high-pressure compressor. This suppresses oil discharge by allowing the refrigerant discharged from the compression unit to the inner space of the casing to move to the lower end of the drive motor by the oil cap and then pass through the drive motor to be discharged to the refrigerant discharge pipe.

However, in Patent Document 2, as the upper end of the oil cap is opened, the oil recovered into the oil cap through between the main frame and the rotating shaft moves directly to the refrigerant discharge pipe through the open upper end of the oil cap, and the inner space of the casing The oil separation effect may be halved.

In addition, in the conventional high-pressure compressor including Patent Document 1 and Patent Document 2, the inner end of the refrigerant discharge pipe communicates with the inner circumferential surface of the casing or is shallowly inserted, so that the movement path of the refrigerant discharged from the compression unit is short and simple. This can be detrimental to separating the oil from the refrigerant.

In addition, in the conventional high-pressure compressor including Patent Document 1 and Patent Document 2, even if the end of the refrigerant discharge pipe is deeply inserted into the casing, the refrigerant discharge pipe is inserted in a straight line or only the inner end is opened. The discharge flow path in the discharge pipe may be generated in one direction and large. As a result, oil flows out together with the refrigerant without flow resistance, and the oil discharge amount may increase.

Korean Patent Publication No. 10-2009-0013042 (published on: 2009.02.04.) Korean Patent Registration No. 10-0686747 (Registration Date: 2007.02.16.)

It is an object of the present invention to provide a hermetic compressor capable of suppressing oil contained in the inner space of the casing from flowing out of the casing through a refrigerant discharge pipe.

Furthermore, an object of the present invention is to provide a hermetic compressor capable of increasing the oil separation effect inside the casing by increasing the flow resistance in the refrigerant discharge pipe.

Furthermore, an object of the present invention is to provide a hermetic compressor that increases flow resistance by complicating the discharge path of the refrigerant toward the refrigerant discharge pipe.

Further, the present invention provides a hermetic compressor capable of suppressing oil discharge by blocking the movement of oil recovered from the compression unit toward the refrigerant discharge pipe through the main bearing surface formed between the outer circumferential surface of the rotating shaft and the inner circumferential surface of the main frame There is a purpose to do that.

Furthermore, an object of the present invention is to provide an oil block enclosing the main bearing surface to provide a hermetic compressor capable of suppressing oil scattering from the main bearing surface from clogging the oil block and heading to the refrigerant discharge pipe.

In order to achieve the object of the present invention, the end of the refrigerant discharge pipe may be inserted deeper than the refrigerant guide passage provided in the compression unit. Through this, the refrigerant passing through the refrigerant guide passage does not directly flow into the refrigerant discharge pipe, but stays in the inner space of the casing for a long time, thereby enhancing the oil separation effect.

In addition, in order to achieve the object of the present invention, a plurality of narrow refrigerant through-holes or slits may be formed on the main surface of the inner end accommodated in the inner space of the casing in the refrigerant discharge pipe. Through this, the oil separation effect may be improved while the refrigerant passes through the narrow refrigerant through hole or slit.

In addition, in order to achieve the object of the present invention, the end of the refrigerant discharge pipe inserted into the inner space of the casing may be formed to be curved or inclined in a direction away from the circulation direction of the refrigerant. Through this, it is possible to suppress the refrigerant circulating in the inner space of the casing from flowing directly into the refrigerant discharge pipe, thereby enhancing the oil separation effect.

In addition, in order to achieve the object of the present invention, an oil cap may be installed between the driving motor and the main frame, and an oil block may be installed at an upper end of the oil cap. The oil block may be installed such that at least a portion of the main frame overlaps in a radial direction. Through this, the scattering of oil recovered from the main frame to the driving motor can be collected to suppress oil discharge.

Specifically, the hermetic compressor according to the present embodiment may include a casing, a driving motor, a rotating shaft, a compression unit, a main frame, a refrigerant suction pipe, and a refrigerant discharge pipe. The casing has an inner space sealed, the drive motor is provided in the inner space of the casing, the rotating shaft is coupled to a rotor of the drive motor, and the compression unit is coupled to the rotary shaft and provided in the inner space of the casing do. The main frame is provided between the driving motor and the compression part, and a shaft support protrusion for supporting the rotation shaft is formed in an annular shape and extends toward the driving motor. The refrigerant suction pipe passes through the casing to communicate with the compression unit and is coupled to the compression unit. The refrigerant discharge pipe may pass through the casing to communicate with the inner space of the casing, and at least one discharge passage may be formed on a main surface of an inner accommodating part belonging to the inner space of the casing. Through this, as a part of the refrigerant passes through the narrow discharge passage and flows into the refrigerant discharge pipe, the oil separation effect may be improved by receiving flow resistance to the refrigerant.

For example, the discharge passage may pass through the main surface of the refrigerant discharge pipe. Through this, while the discharge area of the refrigerant discharge pipe is enlarged, the discharge path is complicated, so that it is possible to suppress the discharge of the refrigerant in an unseparated state in the inner space of the casing.

As another example, the cross-sectional area of the discharge passage portion may be formed to be the same on the side opposite to the side facing the rotational direction of the rotation shaft with respect to the axial center line of the refrigerant discharge pipe. Through this, the refrigerant discharged from the compression unit is evenly distributed on both sides of the refrigerant discharge pipe in the transverse direction, so that the oil separation effect can be improved.

As another example, the cross-sectional area of the discharge passage portion may be formed to be smaller than the opposite side of the side facing the rotational direction of the rotation shaft with respect to the axial centerline of the cross-section of the refrigerant discharge pipe. Through this, it is possible to increase the oil separation effect by increasing the flow resistance of the refrigerant flowing in one circumferential direction in the inner space of the casing.

As another example, the cross-sectional area of the discharge passage may be smaller than the cross-sectional area of the inner circumferential surface of the refrigerant discharge pipe. Through this, the flow resistance of the refrigerant passing through the narrow discharge passage is increased, thereby enhancing the oil separation effect.

For example, the discharge passage portion may be formed in a slit shape by a predetermined depth along the longitudinal direction of the coolant discharge tube at the end of the inner receiving portion of the coolant discharge tube. Through this, it is possible to easily form the discharge passage and increase the flow resistance to the refrigerant, thereby enhancing the oil separation effect.

As another example, the discharge passage portion may be formed to pass through both ends of the refrigerant discharge pipe in the axial direction in a slit shape. Through this, it is possible to increase the flow resistance of the refrigerant by complicating the discharge path of the refrigerant while easily forming the discharge passage.

As another example, the discharge passage portion may be located on an axial center line with respect to the cross section of the refrigerant discharge pipe. Through this, since both side surfaces of the discharge passage are equally formed, the strength of the refrigerant discharge pipe can be maintained while forming the discharge passage in a slit shape.

As another example, a transverse width of the discharge passage may be formed to be smaller than a cross-sectional width of the refrigerant discharge pipe. Through this, it is possible to increase the oil separation effect by suppressing excessive flow of the refrigerant through the discharge passage while sufficiently securing the area of the discharge passage.

For example, the inner accommodating portion of the refrigerant discharge pipe may be formed such that an end surface thereof faces an axial center of the rotation shaft. Through this, the refrigerant discharge pipe can be easily assembled.

For example, the inner accommodating portion of the refrigerant discharge pipe may be formed such that an end surface thereof faces an eccentric direction with respect to the axial center of the rotation shaft. Through this, while assembling the refrigerant discharge pipe easily, it is possible to increase the oil separation effect by complicating the discharge path of the refrigerant.

As another example, the inner receiving portion of the refrigerant discharge pipe may be curved or bent in the rotational direction of the rotation shaft. Through this, it is possible to delay the refrigerant flowing in the circumferential direction in the inner space of the casing from flowing into the refrigerant discharge pipe, so that oil is smoothly separated from the refrigerant.

In addition, the hermetic compressor according to another embodiment may include a casing, a driving motor, a rotating shaft, a compression unit, a main frame, a refrigerant suction pipe, and a refrigerant discharge pipe. The casing has an inner space sealed, the drive motor is provided in the inner space of the casing, the rotating shaft is coupled to a rotor of the drive motor, and the compression unit is coupled to the rotary shaft and provided in the inner space of the casing do. The main frame is provided between the driving motor and the compression part, and a shaft support protrusion for supporting the rotation shaft is formed in an annular shape and extends toward the driving motor. The refrigerant suction pipe passes through the casing to communicate with the compression unit and is coupled to the compression unit. The refrigerant discharge pipe may pass through the casing and communicate with the inner space of the casing, and the end surface of the inner receiving part belonging to the inner space of the casing may be formed to face an eccentric direction with respect to the axial center of the rotating shaft. Through this, while assembling the refrigerant discharge pipe easily, it is possible to increase the oil separation effect by complicating the discharge path of the refrigerant.

For example, the inner receiving portion of the refrigerant discharge pipe may be curved or bent in the rotational direction of the rotation shaft. Through this, it is possible to delay the refrigerant flowing in the circumferential direction in the inner space of the casing from flowing into the refrigerant discharge pipe, so that oil is smoothly separated from the refrigerant.

For example, the compression unit is provided with a refrigerant guide passage for guiding the refrigerant compressed in the compression chamber to the inner space of the casing, the outlet side end of the refrigerant guide passage communicates with the space in which the refrigerant discharge pipe is accommodated, The refrigerant discharge pipe may be formed so that an inner end accommodated in the inner space of the casing is located closer to or equal to the rotation shaft than an outlet end of the refrigerant guide passage. Through this, the discharge path of the refrigerant discharged from the compression unit and moving adjacent to the inner circumferential surface of the casing is complicated, and thus the refrigerant circulates for a long time in the inner space of the casing, thereby improving the oil separation effect.

As another example, the inner end of the refrigerant discharge pipe may be axially overlapped with a stator coil provided in the driving motor between the driving motor and the compression unit. Through this, the inner end of the refrigerant discharge pipe is positioned far from the refrigerant guide passage adjacent to the inner circumferential surface of the casing, thereby complicating the formation of the refrigerant discharge path. .

In the scroll compressor according to the present embodiment, at least one discharge passage may be formed on a main surface of a refrigerant discharge pipe belonging to an inner space of a casing. Through this, as a part of the refrigerant passes through the narrow discharge passage and flows into the refrigerant discharge pipe, the oil separation effect may be improved by receiving flow resistance to the refrigerant.

In addition, in the scroll compressor according to the present embodiment, the discharge passage may pass through the main surface of the refrigerant discharge pipe. Through this, while the discharge area of the refrigerant discharge pipe is enlarged, the discharge path is complicated, so that it is possible to suppress the discharge of the refrigerant in an unseparated state in the inner space of the casing.

Also, in the scroll compressor according to the present embodiment, the cross-sectional area of the discharge passage may be the same on the side facing the rotational direction of the rotating shaft and the opposite side with respect to the axial center line of the refrigerant discharge pipe. Through this, the refrigerant discharged from the compression unit is evenly distributed on both sides of the refrigerant discharge pipe in the transverse direction, so that the oil separation effect can be improved.

Also, in the scroll compressor according to the present embodiment, the cross-sectional area of the discharge passage may be formed so that the side facing the rotational direction of the rotating shaft is smaller than the opposite side with respect to the axial center line of the cross section of the refrigerant discharge pipe. Through this, it is possible to increase the oil separation effect by increasing the flow resistance of the refrigerant flowing in one circumferential direction in the inner space of the casing.

In addition, in the scroll compressor according to the present embodiment, the discharge passage portion may be formed in a slit shape along the longitudinal direction of the refrigerant discharge tube at the end of the inner receiving portion of the refrigerant discharge tube. Through this, it is possible to easily form the discharge passage and increase the flow resistance to the refrigerant, thereby enhancing the oil separation effect.

In addition, in the hermetic compressor according to the present embodiment, the refrigerant discharge pipe is long inserted into the inner space of the casing, and may be located closer to or equal to the rotation shaft than the outlet end of the refrigerant guide passage provided in the main frame. Through this, the discharge path of the refrigerant discharged from the compression unit and moving adjacent to the inner circumferential surface of the casing is complicated, and thus the refrigerant circulates for a long time in the inner space of the casing, thereby improving the oil separation effect.

In addition, in the hermetic compressor according to the present embodiment, the inner end of the refrigerant discharge pipe may be formed to face an eccentric direction with respect to the axial center of the rotating shaft in the inner space of the casing. Through this, it is possible to form a complicated refrigerant discharge path while assembling the refrigerant discharge pipe easily.

In addition, in the hermetic compressor according to the present embodiment, the refrigerant discharge pipe may be bent curvedly or obliquely along the rotational direction of the rotating shaft in the inner space of the casing. Through this, it is possible to delay the refrigerant flowing in the circumferential direction in the inner space of the casing from flowing into the refrigerant discharge pipe, so that oil is smoothly separated from the refrigerant.

1 is a schematic diagram showing a refrigeration cycle device to which an upper compression type scroll compressor according to the present embodiment is applied;
2 is a cross-sectional view showing an upper compression type scroll compressor according to the present embodiment;
3 is an enlarged cross-sectional view of a part of the transmission part and a part of the compression part in FIG. 2;
4 is a cross-sectional view showing a part of a scroll compressor to which a refrigerant discharge pipe of another embodiment is applied in FIG. 2;
5 is an enlarged cross-sectional view of the refrigerant discharge pipe in FIG. 4;
6 is a sectional view "IV-IV" of FIG. 5;
7 is a schematic diagram showing the oil separation effect when the refrigerant discharge pipe according to FIG. 4 is applied;
8 is a sectional view "IV-IV" of FIG. 5 shown to explain another embodiment of the refrigerant discharge pipe;
9 is a cross-sectional view showing a part of a scroll compressor to which a refrigerant discharge pipe of another embodiment is applied in FIG. 2;
10 is an enlarged cross-sectional view of the refrigerant discharge pipe in FIG. 9;
11 is a "V-V" front sectional view of FIG. 10;
12 is a schematic diagram showing the oil separation effect when the refrigerant discharge pipe according to FIG. 9 is applied;
13 is a cross-sectional view showing a part of a scroll compressor to which a refrigerant discharge pipe of another embodiment is applied in FIG. 2;
14 is an exploded perspective view of the oil guide according to the present embodiment of FIG.
15 is a broken perspective view showing the oil guide according to FIG. 14 is assembled to the rotating shaft;
16 is a cross-sectional view of "VI-VI" of FIG. 15;
17 is a sectional view of "VII-VII" of FIG. 16;
18 is a front sectional view of "VI-VI" of FIG. 15 shown to explain another embodiment of the oil guide;
19 is a cross-sectional view showing another embodiment of the oil guide;
20 is a cross-sectional view showing another embodiment of the oil guide.

Hereinafter, a hermetic compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

As described above, in a typical hermetic compressor, the driving motor and the compression unit are installed together in the inner space of the casing and coupled to the rotating shaft. Alternatively, it may be classified as a high-pressure hermetic compressor.

In the high-pressure hermetic compressor, the refrigerant discharged from the compression unit does not move directly to the refrigerant discharge pipe, but circulates as much as possible in the inner space of the casing and then moves to the refrigerant discharge pipe, thereby suppressing oil discharge. On the other hand, the oil that has been lubricated for the compression part is returned to the oil storage space of the casing as quickly as possible, thereby suppressing oil discharge together with the refrigerant circulating in the inner space of the casing.

The present embodiment relates to an oil discharge suppressing device for preventing oil contained in an inner space of a casing from flowing out through a refrigerant discharge pipe in a high-pressure hermetic compressor. Hereinafter, a high-pressure scroll compressor will be described as an example. However, the oil discharge suppressing device according to the present embodiment is not applied only to the scroll compressor. For example, the compression unit may also be applied to a rotary compressor consisting of rollers and vanes.

In addition, the high-pressure scroll compressor may be divided into an upper compression type and a lower compression type according to the installation position of the compression unit. In the former, the compression unit is installed above the driving motor, and in the latter, the compression unit is installed below the driving motor. This embodiment will be mainly described with an upper compression type scroll compressor.

1 is a schematic diagram showing a refrigeration cycle device to which an upper compression type scroll compressor according to the present embodiment is applied.

Referring to FIG. 1 , in the refrigeration cycle device to which the scroll compressor according to the present embodiment is applied, the compressor 10 , the condenser 20 , the expander 30 , and the evaporator 40 form a closed loop. That is, the condenser 20 , the expander 30 , and the evaporator 40 are sequentially connected to the discharge side of the compressor 10 , and the discharge side of the evaporator 40 is connected to the suction side of the compressor 10 .

Accordingly, the refrigerant compressed in the compressor 10 is discharged toward the condenser 20, and the refrigerant passes through the expander 30 and the evaporator 40 in sequence and is sucked back into the compressor 10 to repeat a series of processes. do.

2 is a cross-sectional view illustrating an upper compression type scroll compressor according to the present embodiment, and FIG. 3 is an enlarged cross-sectional view of a part of the electric part and a part of the compression part in FIG. 2 .

2 and 3 , in the high-pressure scroll compressor (hereinafter, described as a scroll compressor) according to the present embodiment, the driving motor 120 is installed in the lower half of the casing 110 , and the driving motor 120 . A compression unit is installed on the upper side of the The compression unit includes the fixed scroll 140 and the orbiting scroll 150, and in some cases, with the orbiting scroll 150 interposed therebetween, the main frame is provided on the opposite side of the fixed scroll 140 to support the orbiting scroll 150 130 may also be included. Hereinafter, the compression part may be defined as including the fixed scroll 140 and the orbiting scroll 150 .

The casing 110 according to the present embodiment may include a cylindrical shell 111 , an upper cap 112 , and a lower cap 113 . Accordingly, the inner space 110a of the casing 110 is an upper space 110b provided inside the upper cap 112 based on the flow order of the refrigerant, and an intermediate space provided inside the cylindrical shell 111 ( 110c) and a lower space 110d provided inside the lower cap 113 . Hereinafter, the upper space 110b may be defined as a discharge space, the intermediate space 110c may be defined as an oil separation space, and the lower space 110d may be defined as an oil storage space, respectively.

The cylindrical shell 111 has a cylindrical shape with both upper and lower ends open, and the driving motor 120 and the main frame 130 are respectively inserted into and fixed to the lower and upper halves along the axial direction on the inner circumferential surface of the cylindrical shell 111 .

The intermediate space 110c of the cylindrical shell 111, specifically, between the driving motor 120 and the main frame 130, the refrigerant discharge pipe 116 penetrates and is coupled. The refrigerant discharge pipe 116 may be directly inserted into and welded to the cylindrical shell 111 , but an intermediate connecting pipe 117 made of the same material as the normal cylindrical shell 111 is inserted into the cylindrical shell 111 . is welded, and a refrigerant discharge pipe 116 made of copper is inserted into the intermediate connection pipe 117 and welded.

One end of the refrigerant discharge pipe 116 may be connected to the inner space 110a of the casing 110 , and the other end may be connected to the inlet of the condenser 20 constituting the refrigeration cycle device. In other words, in this embodiment, even if the oil recovery unit (not shown) is not provided in the middle of the refrigerant discharge pipe 116 or even if the oil recovery unit is provided, it will be provided with a very small size than the oil recovery unit disclosed in Patent Document 1 described above. can Therefore, it can be understood that the refrigerant discharge pipe 116 is directly connected to the condenser 20 hereinafter.

The refrigerant discharge pipe 116 may be inserted by a predetermined length into the inner space 110a of the casing 110 . A portion of the refrigerant discharge pipe 116 inserted into the inner space 110a of the casing 110 is defined as an inner accommodating part 1161 , and the inner accommodating part 1161 of the refrigerant discharge pipe 116 is the driving motor 120 . ) and the main frame 130 , more precisely, the stator coil 1212 of the driving motor 120 may be inserted between the upper end and the lower surface of the main frame 130 . Accordingly, the refrigerant discharge pipe 116 can be deeply inserted into the inner space 110a of the casing 110 without interfering with the stator coil 1212 . The refrigerant discharge pipe 116 including the shape of the inner accommodating part 1161 will be described again later.

The upper cap 112 is coupled to cover the opened top of the cylindrical shell 111 . The upper cap 112 has a refrigerant suction pipe 115 coupled therethrough, and the refrigerant suction pipe 115 passes through the upper space 110b of the casing 110 and is directly connected to the suction chamber (unsigned) of the compression unit to be described later. . Accordingly, the refrigerant may be supplied to the suction chamber through the refrigerant suction pipe 115 .

The lower cap 113 is coupled to cover the opened lower end of the cylindrical shell 111 . The lower space 110d of the lower cap 113 forms a storage space, and a preset amount of oil may be stored in the oil storage space. The lower space 110d constituting the oil storage space may communicate with the upper space 110b and the intermediate space 110c of the casing 110 through an oil return passage (unsigned). Accordingly, the oil separated from the refrigerant in the upper space 110b and the intermediate space 110c and the oil recovered after being supplied to the compression unit pass through the oil recovery hole 1221b of the rotor 122 to be described later in the oil storage space. It may be recovered and stored in the lower space 110d that forms.

2 and 3, the driving motor 120 according to the present embodiment is installed in the lower half of the intermediate space 110c constituting the high-pressure part of the inner space 110a of the casing 110, the stator 121 and It includes a rotor 122 . The stator 121 is fixed to the inner wall surface of the cylindrical shell 111 by hot pressing, and the rotor 122 is rotatably provided inside the stator 121 .

The stator 121 includes a stator core 1211 and a stator coil 1212 .

The stator core 1211 is formed in a cylindrical shape and is fixed to the inner circumferential surface of the cylindrical shell 111 by hot pressing. The stator coil 121a is wound on the stator core 1211 , and is electrically connected to an external power source through a terminal (unsigned) coupled through the casing 110 .

The rotor 122 includes a rotor core 1221 and a permanent magnet 1222 .

The rotor core 1221 is formed in a cylindrical shape, and is rotatably inserted into the stator core 1211 with a predetermined gap therebetween. The permanent magnets 1222 are embedded in the rotor core 1222 at predetermined intervals along the circumferential direction.

In addition, a shaft fixing hole 1221a into which the rotating shaft 125 is press-fitted is formed in the center of the rotor core 1221, and at least one oil return hole 1221b is formed around the shaft fixing hole 1221a. can For example, a plurality of oil return holes 1221b may be formed along the circumference of the shaft fixing hole 1221a, and the plurality of oil return holes 1221b may have the same inner diameter. However, in some cases, the plurality of oil return holes 1221b may be formed with different inner diameters. The oil return hole will be explained later along with the oil guide.

Referring to FIG. 2 , the rotation shaft 125 according to the present embodiment is press-fitted to the rotor 122 and coupled thereto. The upper end of the rotating shaft 125 is rotatably inserted into the main frame 130 to be described later and supported in the radial direction, and the lower end of the rotating shaft 125 is rotatably inserted into the subframe 118 in the radial and axial directions. is supported

Specifically, the rotation shaft 125 may include a main shaft portion 1251 , a main bearing portion 1252 , a sub bearing portion 1253 , and an eccentric portion 1254 .

The main shaft portion 1251 is a portion forming the middle of the rotation shaft 125 , and is press-fitted into the shaft fixing hole 1221a provided in the rotor core 1221 and coupled thereto. A balance weight 180 to be described later may be press-fitted to the upper end of the main shaft portion 1251 , that is, a portion extending from the main bearing portion 1252 . The balance weight will be explained later along with the oil guide.

The main bearing unit 1252 is a portion forming the upper end of the rotation shaft 125 , and may be rotatably inserted into the main bearing 171 provided in the main frame 130 to be described later and supported in the radial direction. The outer diameter of the main bearing part 1252 may be larger than the outer diameter of the main shaft part 1251 . Accordingly, a portion in which the main bearing portion 1252 extends from the main shaft portion 1251 may be formed to have a step difference.

The sub-bearing part 1253 is a portion forming the lower end of the rotation shaft 125 , and may be rotatably inserted into the sub-bearing 172 provided in the sub-frame 118 to be radially supported. The outer diameter of the sub-bearing part 1253 may be smaller than the outer diameter of the main shaft part 1251 . Accordingly, a thrust bearing surface supported in the axial direction by the subframe 118 may be formed with a step difference between the main shaft portion 1251 and the sub-bearing portion 1253 .

The eccentric portion 1254 is a portion into which the rotation shaft coupling portion 152 of the orbiting scroll 150 to be described later is inserted, and may be formed inside the main bearing portion 1252 . For example, the eccentric part 1254 is formed to be recessed by a predetermined depth from the upper end of the main bearing part 1252, and the center of the eccentric part 1254 is the center of the main bearing part 1252 (that is, the axial center). It may be formed eccentrically. Accordingly, the rotational force of the driving motor 120 is transmitted to the orbiting scroll 150 through the eccentric portion 1254, so that the orbiting scroll 150 can orbit.

An eccentric bearing 173 may be provided on the inner circumferential surface of the eccentric part 1254 . The eccentric bearing 173 may be formed of a bush bearing like the main bearing 171 and the sub bearing 172 . Although not shown in the drawings, it may be inserted into the outer peripheral surface of the rotating shaft coupling portion 152 of the orbiting scroll 150 to be described later.

In addition, a refueling hole 1255 may be formed inside the rotating shaft 125 to penetrate between both ends of the rotating shaft 125 . The oil supply hole 1255 may be formed by penetrating from the lower end of the rotation shaft 125 to the bottom surface of the eccentric portion 1254 . Accordingly, the oil stored in the lower space 110d constituting the oil storage space may be supplied to the inside of the eccentric portion 1254 through the oil supply hole 1255 .

In addition, an oil pickup 126 may be installed at the lower end of the rotating shaft 125 , precisely at the lower end of the oil supply hole 1255 . The oil pickup 126 may be installed to be submerged in the oil stored in the oil storage space 110d. Accordingly, the oil stored in the oil storage space 110d may be pumped by the oil pickup 126 and sucked through the oil supply hole 1255 .

2 and 3 , the main frame 130 according to the present embodiment is installed on the upper side of the driving motor 120 and fixed to the inner wall surface of the cylindrical shell 111 by hot pressing or by welding. Accordingly, the main frame 130 is usually formed of cast iron.

The main frame 130 includes a main flange part 131 and a shaft support protrusion 132 .

The main flange part 131 is formed in an annular shape and is accommodated in the intermediate space 110c of the cylindrical shell 111 . For example, the outer circumferential surface of the main flange portion 131 may be formed in a circular shape to be in close contact with the inner circumferential surface of the cylindrical shell 111 . In this case, at least one oil return hole (not shown) penetrating in the axial direction may be formed between the outer circumferential surface and the inner circumferential surface of the main flange part 131 .

In addition, at least one frame fixing protrusion (unsigned) may be formed to extend in a radial direction on the outer circumferential surface of the main flange part 131 . The outer peripheral surface of the frame fixing protrusion may be fixed in close contact with the inner peripheral surface of the cylindrical shell 111 . In this case, the frame fixing protrusions are spaced apart in the circumferential direction to form a second discharge passage groove 1311 penetrating between both sides of the main flange portion 131 in the axial direction. Accordingly, the upper end of the second discharge passage groove 1311 communicates with the first discharge passage groove 1421 of the fixed scroll 140 to be described later, and the lower end of the second discharge passage groove 1311 is a refrigerant discharge pipe 116 . It may be communicated to the communicating intermediate space 110c.

The shaft support protrusion 132 extends from the center of the main flange part 131 toward the driving motor 120 , and the outer diameter of the shaft support protrusion 132 is smaller than the inner diameter of the oil block 192 to be described later. Accordingly, the shaft support protrusion 132 is accommodated at a predetermined interval in an oil block 192 to be described later that surrounds the shaft support protrusion 132 .

A shaft support hole 1321 is formed inside the shaft support protrusion 132 . The shaft support hole 1321 may be formed through both sides of the main flange part 131 in the axial direction. Accordingly, the main flange portion 131 may be formed in an annular shape.

The shaft support hole 1321 has the same inner diameter at both ends in the axial direction, and the main bearing 171 may be inserted and fixed in the shaft support hole 1321 . The main bearing 171 may be formed of a bush bearing. Accordingly, the inner circumferential surface of the shaft support hole 1321 , precisely the inner circumferential surface of the main bearing 171 , forms the main bearing surface 171a together with the outer circumferential surface of the main bearing part 1252 provided on the rotating shaft 125 . The main bearing surface will be described later along with the oil guide.

2 and 3 , the fixed scroll 140 according to the present embodiment may include a fixed end plate 141 , a fixed side wall portion 142 , and a fixed wrap 143 .

The fixed end plate 141 may be formed in a disk shape. The outer circumferential surface of the fixed end plate 141 may be formed to be in close contact with the inner circumferential surface of the upper cap 112 forming the upper space 110b or may be formed to be spaced apart from the inner circumferential surface of the upper cap 112 .

In addition, a suction port 1411 that penetrates in the axial direction and communicates with the suction chamber (unsigned) is formed at the edge of the fixed end plate 141 , and the upper cap 112 of the casing 110 passes through the suction port 1411 . The refrigerant suction pipe 115 may be inserted and coupled. Accordingly, the refrigerant suction pipe 115 may directly communicate with the suction port 1411 of the fixed scroll 140 through the upper space 110b of the casing 110 .

In addition, a discharge port 1412 and a bypass hole (not shown) are formed in the center of the fixed head plate part 141 , and a discharge valve 145 for opening and closing the discharge port 1412 and a bypass hole are formed on the upper surface of the fixed head plate part 141 . A bypass valve (not shown) for opening and closing the pass hole may be installed. Accordingly, the refrigerant compressed in the compression chamber V is discharged from the upper side of the fixed scroll 140 to the upper space 110b formed in the upper cap 112 .

The fixed side wall part 142 may extend in an annular shape from the edge of the fixed head plate part 141 toward the main frame 130 . Accordingly, the lower surface of the fixed side wall part 142 may be in close contact with the upper surface of the main frame 130 , that is, the upper surface of the main flange part 131 and may be bolted.

At least one first discharge passage groove 1421 may be formed on the outer peripheral surface of the fixed side wall portion 142 . The first discharge passage groove 1421 may be recessed from the outer circumferential surface of the fixed scroll 140 to communicate between both sides of the fixed scroll 140 in the axial direction. For example, the first discharge passage groove 1421 may be formed to communicate with the lower surface of the fixed side wall portion 142 from the upper surface of the fixed end plate 141 . Accordingly, the upper end of the first discharge passage groove 1421 communicates with the upper space 110b, and the lower end of the first discharge passage groove 1421 is the second discharge passage groove 1311 provided in the main frame 130. It can be communicated to the top.

The fixed wrap 143 may extend from the lower surface of the fixed end plate 141 toward the orbiting scroll 150 . The fixing wrap 143 may be formed in various shapes, such as an involute. The fixed wrap 143 may be engaged with a revolving wrap 153 to be described later to form a pair of compression chambers V.

2 and 3 , the orbiting scroll 150 according to the present embodiment may include a turning mirror plate part 151 , a rotation shaft coupling part 152 , and a turning wrap 153 .

The turning mirror plate part 151 is formed in a disk shape, is supported in the axial direction by the main frame 130 , and is provided to rotate between the main frame 130 and the fixed scroll 140 .

The rotation shaft coupling portion 152 may extend from the geometric center of the orbiting scroll 150 toward the eccentric portion 1254 of the rotation shaft 125 . The rotating shaft coupling part 152 may be rotatably inserted into the eccentric part 1254 of the rotating shaft 125 . Accordingly, the orbiting scroll 150 is rotated by the eccentric portion 1254 of the rotation shaft 125 and the rotation shaft coupling portion 152 .

The orbiting wrap 153 may extend toward the fixed scroll 140 from the upper surface of the turning mirror plate part 151 . The orbiting wrap 153 may be formed in various shapes such as an involute to correspond to the fixed wrap 143 .

In the drawings, an unexplained reference numeral 1161a denotes an inner end of the refrigerant discharge pipe.

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

That is, when power is applied to the driving motor 120 and rotational force is generated, the orbiting scroll 150 eccentrically coupled to the rotating shaft 125 performs a pivoting motion while continuously moving between the rotating scroll 140 and the fixed scroll 140 . A pair of compression chambers (V) are formed.

Then, the volume of the compression chamber V is gradually reduced as it moves from the suction port (or suction chamber) 1411 to the discharge port (or discharge chamber) 1412 while the orbiting scroll rotates.

Then, the refrigerant provided from the outside of the casing 110 is introduced through the suction port 1411 of the fixed scroll 140 through the refrigerant suction pipe 115, and this refrigerant is directed to the final compression chamber by the orbiting scroll 150 compressed as it moves. This refrigerant is discharged into the inner space (upper space) 110a of the casing 110 through the discharge port 1412 of the fixed scroll 140 in the final compression chamber, the first discharge passage groove 1421 and the second discharge passage It moves to the intermediate space 110c of the cylindrical shell 111 or the lower space 110d of the lower cap 113 through the refrigerant guide passage formed by the groove 1311 .

Then, the refrigerant circulates in the inner space 110a of the casing 110 and the oil is separated from the refrigerant, and the oil separated from the refrigerant moves to the oil storage space constituting the lower space 110d of the casing 110 and is stored. A series of processes in which the oil is supplied to the compression unit through the oil pickup 126 and the oil supply hole 1255 of the rotating shaft 125 , while the refrigerant from which the oil is separated is discharged to the outside of the casing 110 through the refrigerant discharge pipe 116 . will repeat

On the other hand, as described above, in the high-pressure scroll compressor, the refrigerant and oil are separated in the inner space 110a of the casing 110 , and the oil is stored, and the refrigerant is stored outside the compressor through the refrigerant discharge pipe 116 , that is, the casing 110 . ) is discharged to the outside. However, the refrigerant discharge pipe 116 communicates with the intermediate space 110c located between the driving motor 120 and the compression unit, that is, between the upper space (discharge space) 110b and the lower space (reservoir space) 110d. Accordingly, the oil discharged to the upper space 110b together with the refrigerant may not be sufficiently separated from the refrigerant and may be discharged from the intermediate space 110c to the refrigerant discharge pipe 116 . As a result, the amount of oil discharged from the compressor may increase, and friction loss in the compression unit may increase.

In consideration of this, a separate oil separation member (not shown) may be installed around the refrigerant discharge pipe 116 , but this may increase the number of parts and increase the manufacturing cost. Accordingly, in the present embodiment, by appropriately forming the shape of the refrigerant discharge pipe 116 , it is possible to increase the oil separation effect without installing a separate oil separation member around the refrigerant discharge pipe 116 .

Referring back to FIGS. 2 and 3 , the refrigerant discharge pipe 116 according to the present embodiment is deeply inserted into the inner space 110a of the casing 110 by a predetermined depth. For example, the inner end 1161a of the refrigerant discharge pipe 116 accommodated in the inner space 110a of the casing 110, that is, the end of the inner accommodating part 1161 is the first end forming the outlet side end of the refrigerant guide passage. 2 It may be inserted so as to be located closer to the rotation shaft 125 than the lower end of the refrigerant guide groove 1311 .

Specifically, the insertion depth L1 of the refrigerant discharge pipe 116, defined as the length from the inner circumferential surface of the casing 110 to the inner end 1161a of the refrigerant discharge pipe 116, is from the inner circumferential surface of the casing 110 to the main It is formed to be larger than the radial length L2 to the lower end of the second refrigerant guide groove 1311 provided in the frame 130 .

For example, the refrigerant discharge pipe 116 is, as described above, between the upper end of the stator coil 1212 and the lower surface of the main frame 130, that is, the inner receiving part 1161 of the refrigerant discharge pipe 116 is the stator coil ( 1212) and axially overlapping position. Accordingly, the inner end 1161a of the refrigerant discharge pipe 116 may be located radially away from the lower end of the second refrigerant guide groove 1311 .

As described above, when the inner end 1161a of the refrigerant discharge pipe 116 is deeply inserted into the inner space 110a of the casing 110, the second refrigerant guide groove 1311 forming the outlet side end of the refrigerant guide passage The distance from the lower end to the inner end 1161a of the refrigerant discharge pipe 116 is increased. In other words, the second refrigerant guide groove 1311 is formed adjacent to the inner circumferential surface of the casing, while the inner end 1161a constituting the inlet of the refrigerant discharge pipe 116 is located far from the inner circumferential surface of the casing 110 .

Then, the refrigerant passing through the second refrigerant guide groove 1311 and moving to the intermediate space 110c in which the refrigerant discharge pipe 116 is located is radially toward the inner end 1161a of the refrigerant discharge pipe 116 . have to move long.

Then, as the time or flow path for the refrigerant to flow in the inner space 110a of the casing 110 becomes longer, the oil separation effect in which oil is separated from the refrigerant may be improved. In this way, it is possible to reduce friction loss due to insufficient oil in the compressor.

On the other hand, another embodiment of the refrigerant discharge pipe according to the present embodiment is as follows.

That is, in the above-described embodiment, the refrigerant discharge pipe is formed as a hollow tube having a single discharge passage, but in some cases, the refrigerant discharge tube may be formed in a shape having a plurality of discharge passages.

4 is a cross-sectional view showing a part of the scroll compressor to which the refrigerant discharge pipe of another embodiment is applied in FIG. 2, FIG. 5 is an enlarged cross-sectional view of the refrigerant discharge pipe in FIG. 4, and FIG. "It is a front sectional view, and FIG. 7 is a schematic diagram shown to explain the oil separation effect when the refrigerant discharge pipe according to FIG. 4 is applied.

4 to 6 , the refrigerant discharge pipe 116 according to the present embodiment is formed of a hollow tube, and a discharge passage part ( 1162) may be formed. Through this, it is possible to further increase the effect of separating oil from the refrigerant by forming various discharge paths of the refrigerant.

For example, the refrigerant discharge pipe 116 is formed by passing the discharge passage 1162 through the main surface of the inner accommodating portion 1161 . The discharge passage unit 1162 includes a plurality of discharge through holes passing through the main surface of the refrigerant discharge pipe 116 . The discharge passage 1162 may be formed in various shapes, such as a circle, an oval, or a rectangle.

The discharge passage portion 1162 is a portion constituting the sub-discharge passage of the refrigerant discharge pipe 116 , and may be formed to be smaller than the inner diameter of the hollow portion 116a constituting the main discharge passage of the refrigerant discharge tube 116 . For example, the cross-sectional area of the individual discharge through-holes among the plurality of discharge through-holes constituting the discharge passage unit 1162 may be formed to be smaller than the cross-sectional area of the refrigerant discharge pipe 116 .

Accordingly, a portion of the refrigerant that has moved to the intermediate space 110c flows into the hollow 116a of the refrigerant discharge pipe 116 through the inner end 1161a of the opened refrigerant discharge pipe 116, and the remaining refrigerant flows inside The refrigerant flows into the interior (hollow) of the discharge pipe 116 through the discharge passage 1162 opened in the main surface of the receiving portion 1161. This refrigerant is discharged to the outside of the compressor through the refrigerant discharge pipe (116).

When the plurality of discharge passages 1162 are formed in the inner receiving portion 1161 of the refrigerant discharge pipe 116 as described above, the total effective discharge area may be increased. However, referring to FIGS. 6 and 7 , in the refrigerant discharge pipe 116 according to the present embodiment, the refrigerant discharge path is dispersed and the refrigerant path may be complicated. Through this, the time the refrigerant stays in the inner space 110a of the casing 110 before being discharged to the refrigerant discharge pipe 116 is extended, and the oil separation effect in the compressor can be improved.

In particular, as the inner diameter of the discharge passage 1162 is formed to be smaller than the inner diameter of the refrigerant discharge pipe 116 , the flow resistance in the discharge passage 1162 increases, so that the oil separation effect described above can be further improved.

The discharge passage 1162 according to the present embodiment may be regularly formed along the main surface. In other words, the number or cross-sectional area of the discharge passages 1162 may be uniformly formed along the circumferential direction of the inner accommodating portion 1161 . However, in consideration of the flow direction of the refrigerant, the number or cross-sectional area of the discharge passages 1162 may be different.

In general, the rotating shaft 125 coupled to the rotor 122 in the inner space 110a of the casing 110 rotates in one direction. Accordingly, in the inner space 110a of the casing 110 , a refrigerant airflow in one direction is formed along the rotational direction of the rotating shaft 125 . Accordingly, in the discharge passage 1162 , the density of the discharge passage 1162 on the side facing the direction in which the refrigerant rotates and the discharge passage 1162 on the opposite side may be formed to be different.

8 is a cross-sectional view "IV-IV" of FIG. 5 shown to explain another embodiment of the refrigerant discharge pipe.

Referring to FIG. 8 , in the refrigerant discharge pipe 116 according to the present embodiment, the discharge passages 1162 at both sides in the circumferential direction are formed differently based on the axial center line CL, and discharge from both sides. The total cross-sectional area of the passage portion 1162 may be different.

Specifically, the total cross-sectional area of the first discharge passage portion 1162a may be smaller than the total cross-sectional area of the second discharge passage portion 1162b. Hereinafter, the first discharge passage 1162a may be understood as a discharge passage formed on a side (first side) facing the rotational direction of the rotation shaft 125 , and is a discharge passage on the opposite side (second side). The part may be understood as the second discharge passage part 1162b.

For example, the first discharge passage portion 1162a and the second discharge passage portion 1162b each have a plurality of discharge through holes, and the number of discharge through holes constituting the first discharge passage portion 1162a is the second discharge hole. It may be formed to be less than the number of the discharge through-holes constituting the passage portion 1162b. Accordingly, the density of the first discharge passage portion 1162a provided on the first side surface may be smaller than the density of the second discharge passage portion 1162b provided on the second side surface.

Through this, in this embodiment, the discharge passage portion 1162a on the first side and the discharge passage portion 1162b on the second side of the coolant discharge pipe 116 are formed differently, in consideration of the flow direction of the coolant. The discharge passage portion (first discharge passage portion) 1162a on the side directly colliding with the refrigerant may be formed relatively coarser than the discharge passage portion (second discharge passage portion) 1162b on the opposite side.

Then, under the condition that the cross-sectional area of the entire discharge path including the hollow 116a constituting the main discharge path in the refrigerant discharge pipe 116 and the discharge path portion 1162 constituting the sub discharge path is the same, the refrigerant discharge path is more complex and diverse. can be formed. Through this, the discharge time of the refrigerant may be delayed, thereby further enhancing the effect of separating oil from the refrigerant.

On the other hand, another embodiment of the discharge passage is as follows.

That is, in the above-described embodiment, the discharge passage is formed through the main surface of the inner accommodating portion 1161 of the refrigerant discharge pipe 116, but in some cases, the discharge passage 1162 is the inside of the refrigerant discharge tube 116. It may be formed in the shape of a slit split in the longitudinal direction at the end.

9 is a cross-sectional view showing a portion of a scroll compressor to which a refrigerant discharge pipe of another embodiment is applied in FIG. 2, FIG. 10 is an enlarged cross-sectional view of the refrigerant discharge pipe in FIG. 9, and FIG. V" is a front sectional view, and FIG. 12 is a schematic view for explaining the oil separation effect when the refrigerant discharge pipe according to FIG. 9 is applied.

9 to 11, in the refrigerant discharge pipe 116 according to this embodiment, the inner end 1161a of the refrigerant discharge pipe 116 forms the outlet side end of the refrigerant guide passage as in the above-described embodiment. 2 It may be formed closer to the rotation shaft 125 than the lower end of the refrigerant guide groove 1311 . Since the operation and effect thereof are the same as those of the above-described embodiment, a description thereof will be omitted.

However, the discharge passage 1162 according to the present embodiment may be formed in a slit shape by a predetermined depth along the longitudinal direction of the refrigerant discharge pipe 116 at the inner end 1161a of the refrigerant discharge pipe 116. . Accordingly, the inner end 1161a of the refrigerant discharge pipe 116 constituting the end surface of the inner accommodating portion 1161 may be formed in a shape in which both sides are blocked with the discharge passage 1162 in the center.

The discharge passage 1162 may be formed to be located on the axial center line with respect to the cross section of the refrigerant discharge pipe 116 . In other words, both sides of the discharge passage 1162 in the circumferential direction may be symmetrically blocked. Accordingly, the strength of the refrigerant discharge pipe 116 can be secured while the discharge passage part 1162 is formed in a slit shape in the refrigerant discharge pipe 116 .

Specifically, the discharge passage portion 1162 according to the present embodiment may include an inner surface passage portion 1162c and an upper and lower main surface passage portion 1162d.

The inner surface passage portion 1162c is formed to penetrate in the axial direction (width direction) from the inner end 1161a of the refrigerant discharge pipe 116 , and the upper and lower main surface passage portions 1162d are the inner side of the refrigerant discharge tube 116 . It is formed in a shape split in the radial direction (longitudinal direction) from the main surface constituting the receiving portion 1161 .

The inner surface passage portion 1162c and the main surface passage portion 1162d may be connected to each other and formed in a rectangular parallelepiped shape having a predetermined width and length. Accordingly, the refrigerant discharge pipe 116 has both sides in the axial direction of the inner accommodating part 1161 (ie, the upper surface and the lower surface) and the inner end 1161a of the inner accommodating part 1161 is partially opened, but in the circumferential direction. Both sides may be formed into a closed shape.

11 and 12 , even when the discharge passage 1162 is formed in a slit shape as in the present embodiment, the refrigerant discharge path is complicatedly formed and the refrigerant in the inner space 110a of the casing 110 The discharge is delayed, and thus oil discharge from the compressor is suppressed, thereby reducing frictional losses.

In other words, even in this embodiment, the effective discharge area of the refrigerant discharge pipe 116 is secured while the discharge path of the refrigerant is dispersed, and the area of the discharge path per unit area is narrowed. As a result, as flow resistance increases with respect to the refrigerant flowing into the refrigerant discharge pipe 116 , the oil separation effect from the refrigerant passing through the discharge passage unit 1162 in the refrigerant discharge pipe 116 may be further improved.

Although not shown in the drawings, a plurality of discharge passages 1162 may be formed even in the present embodiment. In this case, the discharge passages 1162 may be formed at equal intervals. The effect is similar to the above-described embodiment in which the discharge passage 1162 is formed of a single slit.

On the other hand, there is another embodiment of the refrigerant discharge pipe as follows.

That is, the refrigerant discharge pipe 116 in the above-described embodiments is formed so that its inner end 1161a faces the axial center O of the rotating shaft 125, but in some cases, the refrigerant discharge pipe 116 The inner end 1161a of the may be formed to face an eccentric direction with respect to the axial center (O) of the rotation shaft (125).

13 is a cross-sectional view illustrating a part of a scroll compressor to which a refrigerant discharge pipe according to another embodiment is applied in FIG. 2 .

13, in the refrigerant discharge pipe 116 according to the present embodiment, the end of the inner accommodating part 1161, that is, the inner end 1161a of the refrigerant discharge pipe 116, is the axial center of the rotating shaft 125 ( O) may be formed to be curved toward the eccentric direction.

For example, in the present embodiment, the refrigerant discharge pipe 116 is in a direction corresponding to the rotational direction of the inner accommodating part 1161 and the rotating shaft 125 (that is, when the rotating shaft rotates clockwise, the inner accommodating part is also clockwise may be formed to be curved. Accordingly, the inner end 1161a of the refrigerant discharge pipe 116 faces the refrigerant flowing in the rotational direction of the rotating shaft 125 .

Then, the refrigerant does not directly flow into the inner end 1161a of the refrigerant discharge pipe 116, but rotates along the curved outer circumferential surface of the refrigerant discharge pipe 116. Then, the discharge time of the refrigerant flowing into the refrigerant discharge pipe 116 from the inner space 110a of the casing 110 is delayed, so that the oil separation effect from the refrigerant can be further improved.

Although not shown in the drawings, the refrigerant discharge pipe 116 may be formed by bending its inner end 1161a in an eccentric direction with respect to the axial center O of the rotating shaft 125 . Even in this case, the effect is similar to that of the previous embodiment.

In addition, although not shown in the drawings, the refrigerant discharge pipe 116 may be assembled obliquely to face the eccentric direction with respect to the axial center O of the rotating shaft 125 while the inner accommodating part 1161 is formed in a straight line. have. Even in this case, the refrigerant discharge pipe 116 may be formed eccentrically in a direction conforming to the rotational direction of the rotating shaft 125, thereby complicating the refrigerant discharge path, thereby enhancing the oil separation effect.

In addition, although not shown in the drawings, the refrigerant discharge pipe 116 has a plurality of discharge through holes or slit-shaped discharge passages 1162 in its inner receiving portion 1161 even when the inner end 1161a thereof is curved or bent. ) can be formed. In these cases, the oil separation effect from the refrigerant can be further improved.

Meanwhile, in the scroll compressor according to the present embodiment, an oil guide 190 may be installed between the driving motor 120 and the main frame 130 . Through this, after lubricating the compression part, the oil is mixed with the refrigerant in the process of being returned to the lower space 110c constituting the storage space through the main bearing surface 171a to the outside of the casing 110 through the refrigerant discharge pipe 116. leakage can be more effectively suppressed.

14 is an exploded perspective view showing the oil guide according to the present embodiment of FIG. 15, FIG. 15 is a perspective view showing the oil guide according to FIG. 14 assembled on the rotating shaft, and FIG. 16 is an exploded perspective view of FIG. Ⅳ" is a sectional view, and FIG. 17 is a sectional view "VII-VII" of FIG. 16 .

14 to 17 , the oil guide 190 according to the present embodiment may include an oil cap 191 and an oil block 192 . The oil cap 191 may extend toward the rotor 122 with respect to the balance weight 180 , and the oil block 192 may extend toward the main frame 130 with respect to the balance weight 180 .

For example, the balance weight 180 may include a fixed mass portion 181 fixed to the rotation shaft 125 , and an eccentric mass portion 182 eccentrically extending from the fixed mass portion 181 .

The fixed mass portion 181 is formed in an annular shape and is fixed to the main shaft portion 1251 of the rotating shaft 125 on the upper side of the rotor 122 , and the eccentric mass portion 182 is on the outer circumferential side of the fixed mass portion 181 . It may extend eccentrically in the radial direction to be formed in a fan-shaped arc shape. Accordingly, the outer diameter of the fixed mass portion 181 may be larger than the outer diameter of the rotating shaft (main shaft portion) 125 and smaller than the outer diameter of the eccentric mass portion 182 .

However, as the oil cap 191 to be described later is coupled to the eccentric mass portion 182 and inserted into the stator coil 1212, the outer diameter of the eccentric mass portion 182 connects the inner circumferential surface of the stator coil 1212. The diameter of the virtual circle, for example, may be formed smaller than the inner diameter of the stator core 1211 .

14 and 15 , the oil cap 191 according to the present embodiment may include an oil guide part 1911 and a cap fixing part 1912 .

The oil guide portion 1911 is formed in a cylindrical shape with both ends open. The upper end of the oil guide portion 1911 is fixedly coupled to the balance weight 180 using a cap fixing portion 1912 to be described later, and the lower end of the oil guide portion 1911 extends toward the upper end of the rotor 122 . In other words, the length of the oil guide portion 1911 may be formed longer than the distance from the upper surface of the balance weight 180 to the upper end of the stator coil 1212 . Accordingly, the lower end of the oil guide portion 1911 forming the lower opening portion 190a of the oil guide 190 may be inserted into the stator coil 1212 .

The inner diameter of the oil guide portion 1911 may be formed to be greater than or equal to the outer diameter of the balance weight 180 , that is, the outer diameter of the eccentric mass portion 182 . Accordingly, the balance weight 180 may be accommodated in the oil guide unit 1911 .

In addition, the inner diameter of the oil guide portion 1911 may be formed to be greater than or equal to the diameter of the imaginary circle whose radius is from the axial center (O) of the rotating shaft 125 to the center (O') of the oil return hole 1221b. have. For example, the inner diameter of the oil guide portion 1911 may be formed to a size that can accommodate all of the oil return holes 1221b inside the oil guide portion 1911 . Accordingly, the oil recovered along the oil guide portion 1911 may move to the oil return hole 1221b and then pass through the oil return hole 1221b to be recovered into the oil storage space 110d. Through this, the oil recovered through the main bearing surface 171a is quickly recovered to the oil storage space 110d, thereby minimizing oil discharge.

The cap fixing part 1912 is bent inwardly toward the upper surface of the balance weight 180 from the upper end of the oil guide part 1911 to form an annular shape. For example, the inner diameter of the cap fixing portion 1912 is formed smaller than the outer diameter of the eccentric mass portion (182). Accordingly, the cap fixing part 1912 may be supported in the axial direction by being placed on the upper surface of the eccentric mass part 182 constituting the upper end of the balance weight 180 .

The cap fixing part 1912 is fastened to the upper surface of the eccentric mass part 182 . For example, a fastening groove 182a is formed on the upper surface of the eccentric mass portion 182, and a through hole 1912a is formed in the cap fixing portion 1912 so as to correspond to the fastening groove 182a of the eccentric mass portion 182 on the same axis. ) is formed. Accordingly, the cap fixing part 1912 may be fastened to the eccentric mass part 182 with a bolt.

Here, the oil block 192 to be described later may be independently formed from the oil guide part 1911 or the cap fixing part 1912 of the oil cap 191 and fixed to the balance weight 180 . In this case, a fastening hole 192a is formed in the oil block 192, and the fastening hole 192a is the same as the through hole 1912a of the cap fixing part 1912 and the fastening groove 182a of the eccentric mass part 182. It may be formed so as to correspond to the axis. Through this, as the oil guide 190 and the oil block 192 are fastened to the balance weight 180 by the same fastening bolt 195, the oil guide 190 including the oil block 192 can be easily assembled.

The inner diameter of the cap fixing portion 1912 is formed smaller than the outer diameter of the eccentric mass portion 182 , and is formed larger than the outer diameter of the fixed mass portion 181 of the balance weight 180 . In other words, it may be formed to be spaced apart by a predetermined distance between the outer peripheral surface of the fixed mass portion 181 and the inner peripheral surface of the cap fixing portion 1912 . Accordingly, even if a part of the intermediate opening 190b of the oil guide 190 made of the inner circumferential surface of the cap fixing part 1912 is blocked by the eccentric mass part 182 of the balance weight 180, the eccentric mass part 182 is deviated. In a section, that is, in a section in which the fixed mass portion 181 is formed in the circumferential direction, it may always be in an open state. Then, the oil guide part 1911 is not completely blocked by the balance weight 180 and partly remains open, so that the oil recovered through the main bearing surface 171a is smoothly guided to the oil return hole 1221b. can be

It is advantageous in terms of recovery of oil scattered from the main bearing surface 171a that the inner diameter of the cap fixing part 1912 is formed as large as possible. However, if the inner diameter of the cap fixing part 1912 is excessively large in a state where the outer diameter of the cap fixing part 1912 (exactly, the outer diameter of the oil guide part) is determined, the width of the cap fixing part 1912 becomes too small. Then, it may be difficult to stably fix the oil block 192 extending from the cap fixing part 1912 . Accordingly, the inner diameter of the cap fixing part 1912 is formed as large as possible so that the area of the intermediate opening 190b of the oil guide 190 is secured, and it is preferable that the oil block 192 is stably fixed. . For example, the inner diameter of the cap fixing portion 1912 may be formed to be approximately half the width of the eccentric mass portion 182 excluding the fixed mass portion 181 .

Meanwhile, the oil block 192 according to the present embodiment is provided at the upper end of the oil cap 191 . In other words, the oil block 192 is a portion forming the upper end of the oil guide 190 , and is provided to extend in the axial direction from the upper end of the oil cap 191 toward the main frame 130 .

14 and 17 , the oil block 192 is formed in an annular shape to surround the main bearing surface 171a, and the upper end of the oil block 192 is higher than or at least equal to the lower end of the main bearing surface 171a. can be In other words, the oil block 192 is formed such that at least a portion of the oil block 192 overlaps the shaft support protrusion 132 forming the main bearing surface 171a in a radial direction so as to surround the main bearing surface 171a. Accordingly, even if the upper end of the oil guide 190, that is, the upper end of the oil block 192 is opened, the oil recovered through the main bearing surface 171a is transmitted through the upper opening 190c of the oil guide 190 through the refrigerant discharge pipe ( 116) can be suppressed.

Specifically, the oil block 192 according to this embodiment extends in the axial direction from the cap fixing part 1912, and the inner diameter of the oil block 192 is larger than the inner diameter of the main bearing surface 171a and the cap fixing part 1912. It is formed to be greater than or equal to the inner diameter. Accordingly, the oil recovered through the main bearing surface 171a may be collected inside the oil cap 191 and smoothly guided to the oil recovery hole 1221b of the rotor 122 .

In addition, the oil block 192 according to the present embodiment is separately manufactured for the oil guide part 1911 or the cap fixing part 1912 and is post-assembled. For example, the oil block 192 is formed in an annular shape and is fastened to the eccentric mass part 182 of the balance weight 180 together with the cap fixing part 1912 in a state that it rests on the upper surface of the cap fixing part 1912. . In this case, the fastening hole 192a of the oil block 192 is formed on the same axis as the through hole 1912a of the cap fixing part 1912 and the fastening groove 182a of the eccentric mass part 182, as described above. The oil block 192 may be fastened to the eccentric mass part 182 by the same fastening bolt 195 together with the cap fixing part 1912 .

In addition, the oil block 192 according to the present embodiment is formed to have a flat inner circumferential surface. For example, the inner circumferential surface of the oil block 192 may have a single inner diameter between both ends in the axial direction. Accordingly, it is possible to easily manufacture the oil block 192 . In addition, it can be easily assembled while maintaining a close distance between the inner peripheral surface of the oil block 192 and the outer peripheral surface of the shaft support hole 1321 facing the same. Through this, it is possible to suppress oil leakage from the inside of the oil guide.

In addition, in the oil block 192 according to this embodiment, the first interval t1 between the inner circumferential surface of the oil block 192 and the outer circumferential surface of the shaft support protrusion 132 facing it is the inner circumferential surface of the oil block 192 and It may be formed to be smaller than the second interval t2 between the outer peripheral surfaces of the fixed mass portion 181 facing them. Accordingly, it is possible to effectively suppress the oil scattering from the lower end of the main bearing surface 171a from being blocked by the oil block 192 and leaking to the outside of the oil guide 190 . Through this, the oil discharge amount from the compressor can be reduced.

As described above, when the oil block 192 is provided on the upper end of the oil guide 190 and the oil block 192 is formed to overlap the shaft support protrusion 132, the oil storage space is provided through the main bearing surface 171a. By suppressing the oil recovered in the step 110d from flowing out of the oil guide 190, it is possible to greatly reduce the oil discharge from the compressor.

In particular, when the inner accommodating part 1161 of the refrigerant discharge pipe 116 accommodated in the inner space 110a of the casing 110 is deeply inserted to the vicinity of the main bearing surface 171a, the main bearing surface 171a ), a portion of the oil recovered through the oil guide 190 is sucked toward the refrigerant discharge pipe 116, so that an oil leakage loss in the compressor may be increased.

However, when the oil block 192 overlapping the main bearing surface 171a in the axial direction is formed on the upper end of the oil guide 190 as in this embodiment, the oil guide 190 surrounding the main bearing surface 171a. Forms a kind of oil barrier, so it is possible to minimize the leakage of oil through the oil guide 190 to the refrigerant discharge pipe 116 . In this way, it is possible to reduce friction loss due to insufficient oil in the compressor.

On the other hand, another embodiment of the oil block is as follows.

That is, in the above-described embodiment, the inner circumferential surface of the oil block 192 is formed to have a single inner diameter, but in some cases, the inner circumferential surface of the oil block 192 may be formed to have a plurality of inner diameters.

18 is a front sectional view of "VI-VI" of FIG. 15 shown to explain another embodiment of the oil guide.

Referring to FIG. 18 , the oil block 192 according to the present embodiment includes an oil sealing unit 1921 and an oil recovery unit 1922 . The oil sealing part 1921 is formed in the upper half of the inner peripheral surface of the oil block 192 , and the oil return part 1922 is formed in the lower half of the inner peripheral surface of the oil block 192 successively in the oil sealing part 1921 .

The oil sealing part 1921 is formed in an annular shape along the inner circumferential surface of the oil block 1921 . The oil sealing part 1921 is formed to have the same radius as the center of the shaft center O so that the distance from the outer diameter of the shaft support protrusion 132 is constant.

The oil return unit 1922 may be formed in an annular shape along the inner circumferential surface of the oil block 1921 . However, since the oil block 1921 is mounted on the upper surface of the eccentric mass portion 182 of the balance weight 180 and coupled, the oil recovery portion 1922 may not need to be formed in the portion overlapping the eccentric mass portion 182. have. Accordingly, the oil recovery unit 1922 may be formed in a circular arc shape, that is, in a portion excluding the eccentric mass portion 182 along the circumferential direction.

The oil return unit 1922 may be formed to have a predetermined depth in the radial direction from the lower edge of the oil block 192 . For example, the oil recovery unit 1922 may be formed to be stepped on the inner circumferential surface of the oil block 192 . Accordingly, the oil sealing unit 1921 may have a first inner diameter, and the oil recovery unit 1922 may have a second inner diameter larger than the first inner diameter.

The oil return unit 1922 may be formed to be higher than or equal to the lower end (exit side end) of the shaft support protrusion 132 . Accordingly, it is possible to suppress the oil scattering from the lower end (end of the outlet side) of the shaft support protrusion 132 from colliding with the oil sealing portion. Through this, it is possible to minimize the leakage of oil toward the upper opening portion 190c along the oil sealing portion 1921, thereby further reducing friction loss due to insufficient oil in the compressor.

Although not shown in the drawings, the oil recovery unit 1922 may be inclined so that the inner diameter is enlarged toward the lower edge. Even in this case, the effect of the oil recovery part may be similar to that of the above-described embodiment.

On the other hand, another example of the oil guide is as follows.

That is, in the above-described embodiments, the oil block 192 is separately formed with respect to the oil cap 191 and post-assembled to the balance weight 180, but in some cases, the oil cap 191 and the oil block 192 are formed. It may be formed as this single body.

19 is a cross-sectional view showing another embodiment of the oil guide.

Referring to FIG. 19 , in the oil guide 190 according to the present embodiment, the oil cap 191 and the oil block 192 may be formed as a single body.

For example, the oil guide portion 1911 constituting the oil cap 191 is formed in a cylindrical shape, and the cap fixing portion 1912 is radially bent from the inner peripheral surface of the upper end of the oil guide portion 1911 to form an annular shape.

The oil block 192 is bent in the axial direction from the inner periphery of the cap fixing part 1912 to form an annular shape. Accordingly, the oil cap 191 including the oil guide portion 1911 and the cap fixing portion 1912 and the oil block 192 may be formed as a modular oil guide 190 composed of a single component.

As described above, the oil guide 190 in which the oil cap 191 and the oil block 192 are made of a single part has a basic configuration and the effect thereof is as described above in which the oil block 192 is post-assembled to the oil cap 191. Since it is the same as the embodiment, a detailed description thereof is replaced with the description in the above-described embodiment.

However, in this embodiment, as the oil block 192 is integrally formed with the oil cap 191, the overall oil guide 190 can be easily manufactured.

In addition, the oil block 192 according to the present embodiment may be formed to have the same thickness as the oil cap 191 . That is, in the above embodiment, in consideration of the fastening width of the oil block 192, a thickness sufficient to fasten the bolt in the radial direction was required, but in this embodiment, it is not necessary to separately fasten the oil block 192. Therefore, the thickness of the oil block 192 is thinly formed. Accordingly, as the thickness of the oil block 192 is formed thinner than in the above-described embodiment, the weight and cross-sectional area of the oil guide 190 may be reduced, thereby improving motor efficiency.

On the other hand, another example of the oil guide is as follows.

That is, in the above-described embodiments, the oil guide is assembled and fixed to the balance weight coupled to the rotating shaft, but in some cases, it may be coupled to a fixing member such as a stator or a main frame.

20 is a cross-sectional view showing another embodiment of the oil guide.

Referring to FIG. 20 , the upper end of the oil guide 190 according to the present embodiment may be fixedly coupled to the lower surface of the main frame 130 .

For example, the oil guide 190 may be formed in a cylindrical shape, and the guide fixing part 196 may be bent at the upper end of the oil guide 190 to extend in a flange shape. The guide fixing part 196 may be bolted to the lower surface of the main frame 130 .

In this case, the guide fixing part 196 of the oil guide 190 may have a flat upper surface and be fixed in close contact with the lower surface of the main frame. The guide fixing part 196 of the oil guide 190 is between the second refrigerant guide groove 1311 and the main bearing surface 171a, that is, the inner end 1161a of the refrigerant discharge pipe 116 and the main bearing surface 171a. ) can be fixed to be located between Accordingly, while the inner end 1161a of the refrigerant discharge pipe 116 and the main bearing surface 171a are completely separated by the oil guide 190, the oil recovered through the main bearing surface 171a is directly transferred to the refrigerant discharge pipe ( 116) can be almost completely prevented.

In addition, as the oil guide 190 is fixedly coupled to the main frame 130 , the overall weight of the rotating body including the rotor 122 can be reduced, so that the motor efficiency can be improved.

10: compressor 20: condenser
30: expander 40: evaporator
110: casing 110a: inner space
110b: upper space (discharge space) 110c: intermediate space (oil separation space)
110d: lower space (low oil space) 111: cylindrical shell
112: upper cap 113: lower cap
115: refrigerant suction pipe 116: refrigerant discharge pipe
116a: hollow 1161: inner receiving portion
1161a: inner end (end surface) 1162: discharge passage part
1162a: first discharge passage 1162b: second discharge passage
1162c: inner surface passage portion 1162d: main surface passage portion
117: intermediate connector 118: subframe
120: drive motor 121: stator
1211: stator core 1212: stator coil
122: rotor 1221: rotor core
1221a: shaft fixing hole 1221b: oil return hole
1222: permanent magnet 125: rotation shaft
1251: main shaft portion 1252: main bearing portion
1253: sub-bearing part 1254: eccentric part
1255: oil supply hole 126: oil pickup
130: main frame 131: main flange part
1311: second refrigerant guide groove 132: shaft support protrusion
1321: shaft support hole 140: fixed scroll
141: fixed end plate 1411: suction port
1412: discharge port 145: discharge valve
142: fixed side wall portion 1421: first refrigerant guide groove
143: fixed wrap 150: orbiting scroll
151: revolving mirror plate part 152: rotation shaft coupling part
153: turning lap 160: oldham ring
171: main bearing 172: sub bearing
173: eccentric bearing 180: balance weight
181: fixed mass part 182: eccentric mass part
183a: fastening groove 190: oil guide
190a: lower opening 190b: middle opening
190c: upper opening 191: oil cap
1911: oil guide part 1912: cap fixing part
1912a: through hole 192: oil block
192a: fastening hole 1921: oil sealing part
1922: oil recovery part 195: fastening bolt
196: guide fixing part CL: axial center line
L1: Insertion depth of refrigerant discharge pipe L2: Radial length of refrigerant guide passage
O: Center of shaft (center of main bearing) O': Center of oil return hole
V: compression chamber

Claims (16)

a casing having an enclosed inner space;
a driving motor provided in the inner space of the casing;
a rotating shaft coupled to the rotor of the driving motor;
a compression unit provided at one axial direction of the driving motor in the inner space of the casing, coupled to the rotation shaft, and having a compression chamber to compress the refrigerant;
a refrigerant suction pipe connected to the compression unit through the casing; and
and a refrigerant discharge pipe passing through the casing and communicating with the inner space of the casing,
The refrigerant discharge pipe,
At least one discharge passage is formed on the main surface of the inner receiving part belonging to the inner space of the casing,
The discharge passage portion,
A hermetic compressor formed in a slit shape by a predetermined depth along the longitudinal direction of the refrigerant discharge pipe at the end of the inner receiving part of the refrigerant discharge pipe. delete delete delete delete According to claim 1,
A hermetic compressor in which a plurality of discharge passages are formed, and the plurality of discharge passages are formed at equal intervals. 7. The method of claim 6,
The discharge passage portion penetrates between both ends of the refrigerant discharge pipe in the axial direction of the hermetic compressor. 7. The method of claim 6,
The discharge passage portion is located on an axial center line with respect to the cross section of the refrigerant discharge pipe. 7. The method of claim 6,
A lateral width of the discharge passage is formed to be smaller than a cross-sectional width of the refrigerant discharge pipe. According to claim 1,
The inner accommodating part of the refrigerant discharge pipe has an end face toward the axial center of the rotating shaft. According to claim 1,
The inner accommodating part of the refrigerant discharge pipe has an end face facing the eccentric direction with respect to the axial center of the rotating shaft. 12. The method of claim 11,
A hermetic compressor in which the inner receiving portion of the refrigerant discharge pipe is curved or bent in the rotational direction of the rotating shaft. delete delete 13. The method according to any one of claims 1, 6 to 12,
The compression unit is provided with a refrigerant guide passage for guiding the refrigerant compressed in the compression chamber to the inner space of the casing,
The outlet side end of the refrigerant guide passage communicates with the space in which the refrigerant discharge pipe is accommodated,
The refrigerant discharge pipe,
A hermetic compressor in which an inner end accommodated in the inner space of the casing is located closer to or equal to the rotation shaft than an outlet end of the refrigerant guide passage. 16. The method of claim 15,
The inner end of the refrigerant discharge pipe,
A hermetic compressor overlapping in an axial direction with a stator coil provided in the driving motor between the driving motor and the compression unit.

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