KR20190000687A - Compressor having enhaced lubrication structre - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor that supplies oil stored in a low oil space to an upper side through a rotary shaft to enable compression oil lubrication and wet sliding part lubrication.
A scroll compressor according to an embodiment of the present invention includes a casing in which oil is stored in a lower oil storage space in a lower portion thereof, a drive motor provided in the casing, a main frame disposed at one side of the drive motor, The orbiting scroll includes a scroll and a orbiting wrap that engages with the fixed lap of the fixed scroll and forms a compression chamber. The orbiting scroll rotates relative to the fixed scroll. The orbiting scroll is coupled to the drive motor and guides the oil contained in the oil storage space of the casing upward And a rotary shaft provided with an oil supply passage and an eccentric portion eccentrically coupled to the orbiting scroll, and an oil supply groove having both axial ends closed on the outer peripheral surface of the eccentric portion.

Description

[0001] COMPRESSOR HAVING ENHACED LUBRICATION STRUCTURE [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a compressor that prevents an oil supplied to an eccentric portion from leaking excessively, thereby improving the overall lubrication performance.

Generally, compressors are applied to vapor compression refrigeration cycles such as refrigerators and air conditioners.

Compressors can be divided into reciprocating, rotary, and scroll types depending on the method of compressing the refrigerant.

In the scroll compressor, the orbiting scroll is engaged with the fixed scroll fixed to the inner space of the hermetically sealed container, thereby forming a compression chamber between the fixed lap of the fixed scroll and the orbiting lap of the orbiting scroll.

Compared with other types of compressors, the scroll compressor can obtain a relatively high compression ratio, and the suction, compression, and discharge strokes of the refrigerant are continuously smoothly connected to each other and widely used for compressing refrigerant in an air conditioner or the like.

The behavior characteristics of the scroll compressor are determined by the shapes of the fixed wraps of the fixed scroll and the orbiting wraps of the orbiting scroll. The stationary wrap and the orbiting wrap may have any shape, but typically have the form of an involute curve that is easy to process. The Involute curve means a curve corresponding to the locus drawn by the end of the thread when the thread wound around the base circle having an arbitrary radius is released.

When the involute curve is used, the thickness of the wrap becomes constant and the volume change rate becomes constant. Therefore, in order to obtain a sufficient compression ratio, the number of turns of the wrap should be increased. However, as the number of wrap increases, the size of the compressor also increases.

On the other hand, the orbiting scroll is usually formed as a disk in the form of a disk, and the above-described orbiting wrap is formed on one side of the end plate. A boss portion having a predetermined height is formed on the other side surface of the hard plate on which the orbiting wrap is not formed. In addition, a rotation shaft coupled to the rotor of the driving unit is eccentrically engaged with the boss unit to swivel the orbiting scroll.

This configuration allows the orbiting wrap to be formed over almost the entire area of the end plate, and the diameter of the end plate for obtaining the same compression ratio can be reduced. However, in this configuration, as the orbiting wrap and the boss portion are spaced apart in the axial direction, the point of action at which the repulsive force of the refrigerant acts at the time of compression and the point of action of the reaction force for canceling the repulsive force are spaced from each other in the axial direction, The repulsive force and the reaction force act on each other, and the orbiting scroll tilts to cause vibration and noise.

As a method for solving this problem, there is a method in which a point where a rotary shaft and an orbiting scroll are coupled is formed on the same plane as a orbiting wrap, such as a scroll compressor (registration number: 10-1059880) The scroll compressor of the present invention has been disclosed. In this type of scroll compressor, the point of action of the repulsive force of the refrigerant and the point of action of the reaction force against the repulsive force act in opposite directions at the same height, thereby solving the problem of the inclination of the orbiting scroll.

When the eccentric portion of the rotary shaft is inserted to a height at which the eccentric portion of the rotary shaft overlaps with the orbiting wrap of the orbiting scroll in the upper compression scroll compressor and the lower compression scroll compressor, the space for forming the orbiting wrap can be reduced compared to a general scroll compressor having the same hard plate area.

On the other hand, in order to improve the bearing performance at a portion where the rotating shaft and the orbiting scroll are coupled, oil for performing the lubrication function must be supplied smoothly.

For example, in a scroll compressor in which the eccentric portion of the rotary shaft is formed on the same plane as the orbiting wrap of the orbiting scroll, high-pressure refrigerant leaked from the compression chamber can be introduced between the eccentric portion and the rotary shaft coupling portion.

However, if high-pressure refrigerant leaking from the compression chamber flows into the space between the eccentric portion and the engaging portion, the refrigerant may block the oil supply hole to delay the oil supply.

In addition, the compressor requires lubrication even in a section other than the eccentric part, and when the oil is concentrated in a specific section, oil may not be supplied smoothly to other sections.

An object of the present invention is to provide a scroll compressor in which oil can be smoothly supplied between an eccentric portion of a rotary shaft and a rotary shaft engaging portion of an orbiting scroll.

Another object of the present invention is to provide a scroll compressor capable of preventing oil from being excessively supplied between the eccentric portion of the rotary shaft and the rotary shaft engaging portion of the orbiting scroll, .

The scroll compressor according to an embodiment of the present invention is characterized in that an oil supply passage for guiding the oil contained in the oil storage space of the casing to an upper side is provided on a rotary shaft and an oil supply hole penetrating from the oil supply passage to the outer peripheral surface of the eccentric portion, And an oil supply groove which is crossed and both ends of which are closed in the axial direction.

Further, the scroll compressor according to the present invention provides a structure in which both ends of the oil supply groove are clogged in order to prevent excessive oil from being supplied to the eccentric portion.

INDUSTRIAL APPLICABILITY The compressor according to the present invention has the effect of smoothly supplying oil to the eccentric portion by preventing the refrigerant from flowing between the eccentric portion of the rotary shaft and the rotary shaft engaging portion of the orbiting scroll.

In addition, the compressor according to the present invention provides a structure for preventing oil supplied to the eccentric portion from flowing out, thereby providing smooth oil supply even in an oil supply required period that is located at the upper portion of the eccentric portion.

1 is a longitudinal sectional view for explaining a structure of a scroll compressor according to an embodiment of the present invention.
FIG. 2 is an enlarged longitudinal sectional view of a compression section of a scroll compressor according to an embodiment of the present invention.
3 is a perspective view showing a rotation axis of a scroll compressor according to an embodiment of the present invention.
FIG. 4 is a perspective view showing a part of the rotation axis of FIG. 3 enlarged from another angle.
5 is a view illustrating a second oil supply groove portion of a scroll compressor according to an embodiment of the present invention.
6 is a cross-sectional view for explaining the relationship between the main gas force (FM) and the oil supply required period between the fixed scroll and the orbiting scroll in the scroll compressor according to the embodiment of the present invention.
Fig. 7 is a view for explaining the position of the oil supply hole in Fig. 6. Fig.
8 and 9 are longitudinal sectional views for explaining a difference in lubrication performance according to the shape of the oil supply groove in the scroll compressor. Fig. 8 shows a structure in which both ends of the oil supply groove are open, Fig. 9 shows a structure in which the lower end of the oil supply groove is closed Fig.
10 is a vertical sectional view for explaining the shape of the oil supply groove and the oil supply performance according to the embodiment of the present invention.
11 is a perspective view illustrating an embodiment in which both ends of the oil supply groove are blocked by connecting a blocking member to an eccentric portion in the scroll compressor according to the present invention.
12 is a longitudinal sectional view showing the structure of an upper compression scroll compressor according to the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a compressor having improved lubrication performance according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

1 is a cross-sectional view illustrating a scroll compressor according to an embodiment of the present invention.

The scroll compressor of the illustrated embodiment corresponds to a hermetic compressor in which a drive motor and a compression section are provided together in a closed casing and corresponds to a lower compression compressor because the compression section is located below the drive motor.

The scroll compressor according to the present embodiment includes a casing 210 for sealing an inner space, a driving motor 220 disposed at an upper portion of the inner space, a compression unit 200 disposed at a lower portion of the driving motor, And a rotation shaft 226 for transmitting the rotational force of the driving motor 220 to the compression unit 200.

Hereinafter, each configuration will be described in more detail.

[Casing (210)]

The casing 210 serves to seal the inner space, and the upper and lower portions may be formed into a closed cylindrical shape.

The casing 210 includes a cylindrical shell 211 corresponding to an intermediate portion thereof, an upper shell 212 coupled to the upper portion of the cylindrical shell 211, and a lower shell 214 coupled to the lower portion of the cylindrical shell 211 .

The inner space of the casing 210 is a lower space of the upper shell 212 and a first space V1 which is the upper side of the driving motor 220 and a second space V1 between the driving motor 220 and the compression unit 200 A third space V3 corresponding to the lower portion of the fixed scroll 250 and the discharge cover 270 and a fourth space V3 corresponding to the lower portion of the discharge cover 270 and the upper portion of the lower shell 214. [ (V4).

The upper shell 212 is provided with a refrigerant discharge pipe 216. The inlet of the refrigerant discharge pipe 216 is disposed in the first space V1.

The refrigerant compressed in the compression unit 200 is discharged to the second space V2 and the refrigerant discharged into the second space V2 passes through the driving motor 220 and moves to the first space V1, And discharged through the refrigerant discharge pipe 216 disposed in the first space V1.

At this time, it is preferable to prevent the oil from flowing out together with the refrigerant through the refrigerant discharge pipe 216. When the oil to be circulated in the compressor flows out through the refrigerant discharge pipe 216, the amount of oil circulating in the compressor is reduced, thereby reducing the effect of lubrication and cooling.

To this end, an oil separator (not shown) for separating the oil can be connected to the refrigerant discharge pipe 216.

The fourth space V4 under the lower shell 214 serves as a storage space for storing the oil. In other words, the fourth space V4 serves as an oil chamber for temporarily storing the oil supplied in the lubricating period required for oil supply within the compressor. During operation of the compressor, the oil stored in the fourth space (V4) is supplied to the oil supply required period and circulated. When the compressor stops, the oil collects in the fourth space (V3).

On the other hand, a refrigerant suction pipe 218, which is a passage through which the refrigerant to be compressed flows, is installed on the side surface of the cylindrical shell 211. The refrigerant suction pipe 218 passes through the side surface of the fixed scroll 250 and is connected to the compression chamber S1.

The refrigerant flowing through the refrigerant suction pipe 218 has a relatively lower pressure than the refrigerant discharged through the refrigerant discharge pipe 216. Hereinafter, the pressure of the refrigerant flowing through the refrigerant suction pipe 218 is referred to as low pressure, the refrigerant discharged through the refrigerant discharge pipe 216 is referred to as high pressure, and the pressure therebetween is referred to as intermediate pressure.

[Driving Motor 220]

The compressor according to the present embodiment is a lower compression type in which a driving motor 220 for driving the compression unit 200 is disposed on the upper side in the internal space of the casing 210. Of course, in the case of the upper compression type compressor, the driving motor is disposed on the lower side in the inner space of the casing 210.

 The drive motor 220 includes a stator 222 and a rotor 224. The stator 222 is formed in a cylindrical shape so that the outer circumferential surface of the stator 222 is fixed to the inner surface of the casing 210. The stator 222 has a plurality of slots formed in its inner circumferential surface along the circumferential direction, and the coil 222a is wound around the slots.

A refrigerant flow path groove 212a may be provided on the outer circumferential surface of the stator 222. [

The refrigerant passage groove 212a serves as a passage for allowing the refrigerant in the second space V2 to move to the first space V1. The coolant channel groove 212a may be formed by cutting a part of the outer circumferential surface of the stator 222 or may be formed in the form of a longitudinal groove on the outer circumferential surface of the stator 222. [

The rotor 224 rotates inside the stator 222 and generates rotational power. The rotary power generated by the rotor 224 is transmitted to the compression unit 200 through the rotary shaft 225. The rotating shaft 225 is coupled to the rotor 224 and rotates integrally with the rotor 224.

[Compression unit 200]

The compression unit 200 includes a main frame 230, a fixed scroll 250, a orbiting scroll 240, and a discharge cover 270.

[Main Frame (230)]

The main frame 230 forms the upper portion of the compression unit 200 and faces the lower portion of the driving motor 220.

The main frame 230 includes a frame end plate portion 232 and a frame side wall portion 231.

The frame holding plate 232 is formed in a substantially circular shape and has a frame bearing part 232a at the center thereof. The frame bearing portion 232a is a portion through which the rotating shaft passes. The frame bearing part 232a may protrude from the upper surface of the frame holding part 232 toward the driving motor 220 and may be rotatably coupled to the main bearing part MB of the rotating shaft 226. [

The frame side wall portion 231 extends to the fixed scroll side and the lower end portion thereof is engaged with the fixed scroll 250. The outer circumferential portion of the frame side wall portion 231 is engaged with the cylindrical shell 211 of the casing 210.

The frame side wall portion 231 has a frame discharging hole 231a penetrating the inside thereof in the axial direction (longitudinal direction). The frame discharge hole 231a provides a passage through which the compressed refrigerant can move from the third space V3 to the second space V2. The frame discharge hole 231a is connected to the fixed scroll discharge hole 256b provided in the fixed scroll 250.

The main frame 230 is coupled to the fixed scroll 250 and the main frame 230 is disposed between the fixed scroll 250 and the orbiting scroll 240 so as to be pivotable.

A back pressure chamber S2 is formed between the bottom surface of the main frame 230 and the orbiting scroll 240. [ The back pressure chamber S2 includes an intermediate pressure region having a pressure between a low pressure and a high pressure. The orbiting scroll 240 is brought into close contact with the fixed scroll 250 by the pressure of the back pressure chamber S2.

Oldham's ring 150 is provided between the main frame 230 and the orbiting scroll 240. The oralling 150 serves to make the orbiting scroll 240 rotate only without turning.

[Fixed scroll (250)]

The fixed scroll 250 includes a fixed plate portion 254, a fixed scroll sidewall portion 255, a fixed lap 251, and a fixed scroll bearing portion 252.

The fixed plate portion 254 has a substantially circular shape. The fixed plate 254 is provided with a discharge port 253 for discharging the refrigerant compressed in the compression chamber S1.

The fixed scroll sidewall portion 255 extends from the outer peripheral portion of the fixed end plate portion 254 to the main frame side and is connected to the main frame side wall portion 231.

The fixed wraps 251 are formed so as to protrude toward the upper side of the fixed plate portion 254. The fixed wraps 251 engage with the orbiting wraps 241 of the orbiting scroll 240 to form the compression chambers S1.

The fixed scroll bearing portion 252 is formed at the center of the fixed plate portion 254 and passes through the rotating shaft 225.

Meanwhile, a discharge cover 270, which accommodates the refrigerant discharged from the compression chamber and divides the third space V3, is coupled to the bottom surface of the fixed scroll 250.

The fixed scroll sidewall portion 255 has a fixed scroll discharge hole 256b connected to the frame discharge hole 231a. The frame discharging hole 231a and the fixed scroll discharging hole 256b allow the refrigerant discharged from the compression chamber S1 to the third space V3 which is the inner space of the discharge cover 270 to flow into the second space V2 .

The fixed scroll bearing portion 252 may protrude from the lower surface of the fixed plate portion 254 toward the oil storage space V4. At this time, the fixed scroll rollers 252 may be bent toward the center side so that the lower end supports the lower end of the sub bearing portion SB of the rotation shaft 226 to form the thrust bearing surface.

[Discharge Cover (270)]

The discharge cover 270 serves to prevent the refrigerant discharged from the discharge port 253 provided in the fixed plate 254 from mixing with the oil stored in the fourth space V4. The discharge cover 270 is coupled to seal the space between the fixed scroll 250 and the bottom surface.

The discharge cover 270 has a through hole 276 through which the oil feeder 271 passes. The oil feeder 271 is coupled to the sub bearing portion SB of the rotary shaft 226 and is immersed in the oil stored in the oil storage space of the casing 210.

[Turn Scroll (240)]

The orbiting scroll 240 is disposed between the main frame 230 and the fixed scroll 250 and is coupled to the eccentric portion EC of the rotating shaft 226. The orbiting scroll 240 pivots by the rotation of the rotating shaft 226.

The orbiting scroll 240 includes a turning plate portion 245, a orbiting wrap 241, and a rotating shaft coupling portion 242.

The turning plate section 245 has a substantially circular shape and faces the fixed plate section 245.

The orbiting wrap 241 protrudes from the bottom surface of the swivel plate 245 toward the fixed plate 245 and engages with the stationary wrap 251. The lower surface of the orbiting wrap (241) is in close contact with the upper surface of the fixed plate portion (254).

The rotary shaft engaging portion 242 is disposed at the center of the turn hard plate portion 245 and is rotatably coupled to the eccentric portion EC of the rotary shaft. The rotary shaft coupling portion 242 is formed at a height that overlaps with the orbiting wrap 241 and is connected to the orbiting wrap 241. The rotary shaft coupling portion 242 is connected to the orbiting wrap 241 to form the compression chamber S1 together with the fixed wraps 251 during the compression process.

When the refrigerant is compressed, the repulsive force of the refrigerant is applied to the fixed lap 251 and the orbiting wrap 241, and a compressive force is applied between the rotary shaft engaging portion 242 and the eccentric portion EC as a reaction force thereto.

The scroll compressor according to the embodiment of the present invention has a structure in which the eccentric part EC of the rotating shaft 226 passes through the turning plate portion 245 of the orbiting scroll 240 and overlaps with the orbiting wrap 241 in the radial direction I have. In this structure, the repulsive force and the compressive force of the refrigerant are applied on the same plane with respect to the turning plate portion 245. Accordingly, since the repulsive force and the compressive force of the refrigerant are canceled each other, the tilting of the orbiting scroll 240 can be reduced.

[Rotation shaft 226]

And serves to transmit the rotational force of the driving motor 220 of the rotary shaft 226 to the compression unit 200 and to provide the oil passage.

The upper portion of the rotary shaft 226 is integrally coupled to the rotor 224 of the drive motor 220 and the lower portion of the rotary shaft 226 is rotatably coupled to the compression portion 200.

The rotary shaft 226 has a main bearing portion MB, a sub bearing portion SB, an eccentric portion EC, an oil supply passage 226a, oil supply holes H1, H2, H3, H4, , And oil supply grooves (G1, G2).

The oil supply passage 226a is provided axially at the center of the rotary shaft. The oil supply passage 226a provides a path through which the oil stored in the oil storage space V4 can move upward.

The main bearing part MB is coupled to the frame bearing part 232a of the main frame 230. The sub bearing portion SB is coupled to the fixed scroll bearing portion 252 of the fixed scroll 250. The eccentric part EC is disposed between the main bearing part MB and the sub bearing part SB and is coupled to the rotary shaft coupling part 242 of the orbiting scroll 240.

The main bearing portion MB, the sub bearing portion SB, and the eccentric portion EC all have a circular cross section. The diameter of each part can be set differently.

The shaft center of the sub bearing portion SB coincides with the shaft center of the main bearing portion MB and the shaft center of the eccentric portion EC is formed to be eccentric with respect to the shaft center of the main bearing portion MB . In other words, the main bearing part MB and the sub bearing part SB are coaxially formed so as to have the same axial center, and the eccentric part EC is formed in a circular shape at an eccentric position with respect to the axial center of the main bearing part MB As shown in Fig.

The eccentric part EC may have an outer diameter smaller than the outer diameter of the main bearing part MB and larger than an outer diameter of the sub bearing part SB. This is for the purpose of improving the assembling property when the rotary shaft 226 is coupled to the compression portion 200.

The oil supply passage 226a is provided inside the rotary shaft 226 to provide a path for supplying the oil stored in the oil storage space V4 to the bearings MB and SB and the eccentric part EC. The bearings MB and SB and the eccentric part EC serve to reduce the frictional force by supplying the oil to the parts where friction with the compression part 200 occurs when the rotary shaft 226 rotates. When the oil is supplied to the friction portion, the frictional force is reduced and the power loss is reduced. The oil also has the effect of cooling the friction zone.

The oil supply passage 226a is provided axially inside the rotary shaft 226, and the oil supply required section (bearing portion, eccentric portion, etc.) requiring oil supply is the outer peripheral surface of the rotary shaft. Therefore, the oil supply hole is formed through the outer peripheral surface of the rotary shaft and connected to the oil supply passage 226a in the oil supply required period.

Specifically, the oil supply hole includes a first oil supply hole (H1 in Fig. 2) formed to penetrate the outer peripheral surface of the main bearing portion MB, a second oil supply hole H2 formed to penetrate the outer peripheral surface of the eccentric portion EC, And a third oil feed hole H3 formed to penetrate the outer peripheral surface of the sub bearing portion SB.

A fourth oil supply hole H4 may be additionally formed through the first small diameter portion 54 that separates the main bearing portion MB and the eccentric portion EC by a predetermined distance. The eccentric portion EC And a fifth oil feed hole H5 passing through the second small diameter portion 55 that separates the sub-bearing portion SB from the sub-bearing portion SB by a predetermined distance. The first small diameter portion 54 and the second small diameter portion 55 are configured to secure the workability of the bearing portions MB and SB and the eccentric portion EC.

2) is formed on the outer circumferential surface of the main bearing portion MB, and the first oil supply groove G1 is formed with a first oil supply groove And can be inclined in the rotation direction or the rotation direction of the rotation shaft. The second oil supply groove (G2 in FIG. 2) may be formed on the outer circumferential surface of the eccentric part EC so as to communicate with the second oil supply hole H2 and extend in the vertical direction. At this time, it is preferable that the second oil supply groove G2 is not formed on the entire height of the eccentric part EC but not on the upper and lower ends.

This is to prevent the oil supplied to the second oil feed groove G2 from flowing out to the outside. If the oil is excessively discharged through the second oil supply groove G2, the oil is not smoothly supplied to the upper portion of the eccentric portion EC of the oil supply passage 226a. When the flow rate of the oil flowing out to the second oil supply hole H2 is increased, the flow rate of the oil supplied to the oil supply channel 226a in the upper oil supply hole H2 is increased, .

Since the main bearing portion MB is provided on the upper portion of the eccentric portion EC and the oil is supplied to the main bearing portion MB through the first oil supply hole H1, When the flow rate of the oil flowing out is increased, the flow rate of the oil supplied to the first lubrication hole H1 is decreased.

The oil supply groove is provided for uniformly supplying oil to the oil supply required section (bearing portion, eccentric portion), and may be provided in the form of a concave groove on the outer peripheral surface of the oil supply required section.

Of course, the second oil supply groove (G2 in FIG. 2) may be formed in a direction parallel to the rotation axis as shown in the drawing, but it may be inclined or spirally formed along the longitudinal direction in some cases.

Further, the second oil supply groove G2 itself may not be formed on the outer circumferential surface of the eccentric portion EC but may be formed on the inner surface of the rotary shaft coupling portion. When the second oil feed groove G2 is formed on the inner surface of the rotary shaft coupling portion, the second oil feed hole H2 formed through the eccentric part EC is formed in the second oil feed groove G2 As shown in Fig.

As a result, the oil guided upward through the oil supply passage 226a is discharged through the first lubrication hole (H1 in Fig. 2) and supplied to the outer peripheral surface of the main bearing portion MB, and the second lubrication hole H2 And is supplied to the outer peripheral surface of the eccentric part EC and discharged through the third oil supply hole H3 and supplied to the outer peripheral surface of the sub bearing part SB in the up and down direction.

The oil guided through the oil supply passage 226a is discharged through the fourth oil supply hole H4 and supplied to the upper surface of the orbiting scroll 240 and discharged through the fifth oil supply hole H5, (240) and the fixed scroll (250). The oil supplied to the inside of the compression chamber has the effect of improving the airtightness of the compression chamber.

Instead of omitting the fourth oil supply hole H4, the first oil supply groove G1 may be formed to the lower end of the main bearing portion MB so that the oil discharged from the fourth oil supply hole H4 may flow into the first small- 54 to the upper surface of the orbiting scroll 240.

Instead of omitting the fifth oil feed hole H5, the third oil feed groove G3 may be formed up to the upper end of the sub bearing portion SB so that the oil discharged from the third oil feed hole H3 flows into the second small- And may be supplied between the orbiting scroll (240) and the fixed scroll (250) through the through hole (55).

An oil feeder 271 for pumping the oil stored in the fourth space V4 may be coupled to the lower end of the rotary shaft 226, that is, the lower end of the sub bearing portion SB.

The oil feeder 271 includes an oil supply pipe 273 inserted into the oil supply passage 226a of the rotary shaft 226 and an oil supply pipe 273 inserted into the oil supply pipe 273, 274).

Here, the oil supply pipe 273 is provided so as to pass through the through hole 276 of the discharge cover 270 and to be submerged in the oil storage space V4.

Although not shown in the drawing, a trochoid pump (not shown) may be coupled to the sub-bearing portion SB to force the oil filled in the oil storage space V4 upward, instead of the oil feeder 271 have.

Although not shown in the drawing, the scroll compressor according to the embodiment of the present invention includes a first axial plate (not shown) for sealing the gap between the upper end of the main bearing portion MB and the upper end of the main frame 230, And a second axial plate (57 in Fig. 3) for sealing the gap between the lower end of the sub-bearing portion SB and the lower end of the fixed scroll 250. [

A balance weight (not shown) for suppressing noise vibration may be coupled to the rotary shaft 226. For reference, the balance weight may be provided between the driving motor 220 and the compression unit 200, that is, in the second space V2.

The operation of the scroll compressor according to the embodiment of the present invention will now be described.

When the power is applied to the driving motor 220, the rotating shaft 226 coupled with the rotor 224 of the driving motor 220 rotates. The orbiting scroll 240 eccentrically connected to the rotary shaft 226 performs the orbiting motion and the compression chamber S1 formed between the orbiting wrap 241 and the stationary wrap 251 moves while changing the volume. At this time, the compression chamber S1 can be formed in several stages in succession as the volume gradually decreases toward the center direction.

The refrigerant is compressed while moving and discharged to the third space V3 through the discharge port 253 of the fixed scroll 250 by the orbiting motion of the orbiting scroll 240. [

The high pressure refrigerant discharged into the third space V3 flows through the fixed scroll 250 and the fixed scroll discharge hole 256b formed to be connected to the main frame 230 and the second space V2 through the frame discharge hole 231a. . The refrigerant discharged to the second space V2 rises to the first space V1 through the refrigerant flow path groove 212a and then flows through the refrigerant discharge tube 216 in the first space V1 to the outside of the casing 210 .

FIG. 3 is a perspective view showing a rotary shaft of a scroll compressor according to an embodiment of the present invention, FIG. 4 is a perspective view showing a part of a rotary shaft of FIG. 3 enlarged from another angle, FIG. 5 is a perspective view of a scroll compressor according to an embodiment of the present invention, And Fig.

As shown in the figure, the rotary shaft 226 of the scroll compressor according to the embodiment of the present invention includes a main bearing part MB which is inserted into the frame bearing part 232a of the main frame 230 and is supported in a radial direction. The rotation shaft 226 has an eccentric part EC at a lower portion of the main bearing part MB and a sub bearing part SB at a lower part of the eccentric part EC.

The main bearing portion MB and the sub bearing portion SB are formed coaxially with each other with the same axis center and that the eccentric portion EC is formed eccentrically in the radial direction with respect to the main bearing portion MB .

An oil supply passage 226a for supplying oil to the bearings MB and SB and the eccentric portion EC is provided in the rotary shaft 226. The oil supply passage 226a is connected to the rotary shaft 226, And extends to the upper side.

The oil supply passage 226a may be formed at a lower end or middle height of the stator 222 at the lower end of the rotation shaft 226 or at a lower end or middle height of the main bearing portion 226 as the compression portion 200 is positioned below the drive motor 220. [ MB may be formed in a hollow shape to a height higher than the upper end of the MB.

In the meantime, oil is sucked through the oil supply passage 226a between the bearing portions MB and SB and the eccentric portion EC, or between the bearings, so that the rising oil can be supplied to the outer peripheral surface of the rotary shaft Holes H1, H2, H3, H4 and H5 and oil supply grooves G1, G2 and G3.

A first small diameter portion 54 is formed between the main bearing portion MB and the eccentric portion EC and a fourth oil supply hole H4 is formed in the first small diameter portion 54. [

A first oil supply groove G1 is formed on an outer circumferential surface of the main bearing portion MB so that oil supplied through the first oil supply hole H1 flows upward along the outer peripheral surface of the main bearing portion MB .

A third oil supply hole H3 communicating with the oil supply passage 226a is formed in the upper portion of the sub bearing portion SB through an outer circumferential surface of the sub bearing portion SB. The third oil supply groove G3 communicating with the second oil supply groove G3 is formed.

The upper end of the third oil supply groove G3 is preferably communicated with the second small diameter portion 55 between the sub bearing portion SB and the eccentric portion EC. The lower end of the second oil supply groove G3 is connected to the communication groove (not shown) provided in the axial plate 229 provided in the sub bearing portion SB and supported around the through hole 341 of the discharge cover 270 229g.

The communication groove 229g may be formed to communicate with the bottom surface of the axial plate 229 in a radial direction. The position of the third fuel supply hole H3 and the shape of the third fuel supply groove G3 are not limited to those shown in the drawings and may be variously formed.

As shown in the figure, the eccentric part EC is formed with a second oil supply hole H2 through which oil flows from the oil supply passage 226a to the outer peripheral surface of the eccentric part EC, A second oil supply groove G2 communicated with the second oil supply hole H2 except for the upper and lower ends thereof may be formed.

The second oil supply hole (H2) may be formed in a radial direction as shown in the drawing, but may be inclined or curved in a forward direction with respect to the rotation direction of the rotary shaft (226). The second oil supply groove G2 may be formed in the longitudinal direction as shown in the drawing, but may be formed to be inclined or spirally formed along the longitudinal direction.

It is preferable that the second oil supply groove G2 is formed in a structure in which both sides are closed as shown in the drawing. To this end, the axial length L1 of the second oil supply groove G2 may be shorter than the axial length L2 of the eccentric portion EC.

The eccentric part EC is also formed as a kind of bearing part. Since the eccentric part EC is formed eccentrically with respect to the axial center at a position overlapping with the orbiting wrap 241 in the radial direction, Can be optimally designed in consideration of the relationship with the pressure ratio.

Therefore, the second oil supply hole (H2) and the second oil supply groove (G2) are formed in positions and shapes that can supply oil quickly and smoothly as compared with other oil supply holes or oil supply grooves, It can be important from the side.

FIG. 6 is a cross-sectional view for explaining the relationship between the main gas force (FM) and the oil supply required period between the fixed scroll and the orbiting scroll in the scroll compressor according to the embodiment of the present invention, and FIG. Fig.

For example, the second lubrication hole H2 may be disposed at a position adjacent to the lubrication required section. When the rotary shaft 226 rotates in the clockwise direction and the pressing direction in which the main gas force FM acts is a positive horizontal coordinate axis as in the illustrated embodiment, Or 3/4 plane.

That is, when the rotary shaft of the scroll compressor rotates clockwise about the axis O, the pressing direction in which the main gas force FM acts is the line connecting the center E of the eccentric portion O ' In the direction perpendicular to the rotational direction.

As shown in Fig. 7, the oil pressure diagram is formed largely within a range of 90 degrees to 180 degrees from the rotational direction side with reference to a line connecting the center of the eccentric portion from the shaft center, and this section is an oil supply required period .

However, if the lubrication hole is formed in the lubrication required period, the oil can not be supplied smoothly. This is because the pressure applied within the oil supply required period is higher than the pressure of the oil flowing through the oil supply passage 226a.

 Therefore, it is preferable that the outlet of the second fuel supply hole (H2) is disposed to avoid the oil supply required section if possible.

However, if the outlet of the second fuel supply hole H2 is disposed too far from the oil supply required section (that is, 2/4 of the figure), it is discharged through the second oil supply hole H2 to the outside of the eccentric part EC The time required for the oil to travel to the oil supply required section is delayed, so that the bearing performance may be deteriorated and wear or frictional loss may be increased.

Therefore, it is preferable that the second fuel supply hole H2 is disposed in the near 1/4 or 3/4 of the fuel supply hole without belonging to the fuel supply required period. This is because, when the line connecting the axial center O of the rotary shaft and the eccentric center O 'of the eccentric part EC is taken as a reference, the range of rotation angle is in the range of 0 degree to 90 degrees or 180 degrees to 270 degrees .

8 and 9 are longitudinal sectional views for explaining a difference in lubrication performance according to the shape of the oil supply groove. Fig. 8 shows a structure in which both ends of the oil supply groove are open. Fig. 9 shows a state in which the oil supply Fig.

8 or 9, when the upper end of the second oil supply groove G2 is opened, the oil supplied through the oil supply passage 226a flows into the second oil supply hole H2 and the second oil supply groove G2 to excessively flow out to the intermediate pressure region, so that the oil can not be smoothly supplied to the first oil feed hole H1 or the fourth oil feed hole H4.

As shown in FIG. 8, when the lower end of the second oil supply groove G2 is opened, the oil contained in the second oil supply groove G2 may flow down due to its own weight, and the eccentric portion EC may not be effectively lubricated.

In addition, when the lower end of the second oil supply groove G2 is open, high-pressure refrigerant leaking from the compression chamber S1 can be moved toward the second oil supply hole H2 through the second oil supply groove G2 have. When the high pressure refrigerant moves to the second oil supply groove G2, the pressure difference between the inside and the outside of the second oil supply hole H2 does not occur due to the refrigerant, or rather the pressure outside the oil supply channel 226a is high, It may not be smoothly supplied to the oil supply groove G2.

Therefore, the lower end of the second oil supply groove G2 is left at the lower end edge of the eccentric part EC, i.e., the end adjacent to the axial end of the orbiting wrap, to cover the lower end of the second oil supply groove G2, (Not shown).

10 is a vertical sectional view for explaining the shape of the oil supply groove and the oil supply performance according to the embodiment of the present invention.

The scroll compressor according to the embodiment of the present invention provides a structure in which the upper and lower ends of the second oil supply groove G2 for supplying oil to the eccentric portion are closed.

In order for the oil supplied through the oil supply passage 226a to flow smoothly into the first or the fourth lubrication hole H1 or H4 disposed above the second lubrication hole H2, And both end portions of the groove G2 are not exposed to the outside of the rotary shaft coupling portion 242. [

The structure in which the upper end of the second oil supply groove G2 is closed prevents the oil supplied to the second oil supply groove G2 from excessively flowing out to the intermediate pressure region. The structure in which the lower end of the second oil supply groove G2 is closed prevents the oil supplied to the second oil supply groove G2 from flowing in the direction of the sub bearing portion SB, And is prevented from flowing into the second fuel feed groove G2.

11 is a perspective view showing an example in which both ends of the oil supply groove are blocked by connecting a blocking member to an eccentric portion in the scroll compressor according to the present invention.

In the above-described embodiment, when the second oil supply groove G2 is formed, an end portion adjacent to both ends in the axial direction of the orbiting wrap is left and a sealing section is integrally formed. However, Is inserted into the eccentric part (EC), and the upper and lower ends of the oil supply groove (G2) are closed to form the cut-off part.

As shown in the figure, a pair of annular grooves 228 are formed at both upper and lower ends of the eccentric part EC of the present embodiment, and a second oil supply groove G2 is formed between the annular grooves 288 .

The blocking member 228a, which is annularly formed in the annular groove 228, may be press-fitted into the second oil supply groove G2 to block both ends of the second oil supply groove G2 to form a blocking portion.

The thickness of the blocking member 228a should be equal to or slightly thinner than the depth of the annular groove 228 to prevent degradation of bearing performance. The thickness of the blocking member 228a should be such that the outer circumferential surface of the blocking member 228a is positioned higher than the bottom of the second fuel supply groove G2 so that both end portions of the second fuel supply groove G2 Can be blocked.

The blocking member may be formed in any shape as long as it can block both ends of the oil supply groove formed in a block shape as well as an annular shape and adhered to the oil supply groove or screwed together so that the screw head acts as a blocking member.

Meanwhile, the lubrication structure according to the present invention is also applicable to an upper compression scroll compressor.

12 shows a scroll compressor according to another embodiment of the present invention.

The upper compression scroll compressor according to the present embodiment has a structure in which a driving motor 320 is installed on the lower side of the inside of the casing 310 and a compression unit 300 is installed on the upper side of the driving motor 320 .

The compression unit 300 includes a fixed scroll 350, a main frame 360, and an orbiting scroll 370.

The fixed scroll (350) has a fixed lap (352) and is coupled to the casing (310). Is disposed on the fixed scroll (350) of the main frame (360) and is coupled to the casing (310). The orbiting scroll 370 has a orbiting wrap 372 and is disposed between the main frame 360 and the fixed scroll 350.

The orbiting scroll 370 is provided with a rotation axis coupling portion 373 such that the eccentric portion EC of the rotation shaft 326 coupled to the rotor of the driving motor 320 is eccentrically connected. The rotary shaft coupling portion 373 is formed so that the eccentric portion EC can overlap with the compression chamber S1 in the radial direction.

An oil supply passage 326a is formed in the rotation shaft 326 from the lower end to the upper end. The oil supply passage 326a is preferably formed to a predetermined height from the lower end of the rotary shaft 326, that is, to an intermediate position of the eccentric part EC. The eccentric part EC is formed with a second oil supply hole H2 passing through the oil supply passage 226a from the outer circumferential surface of the eccentric part EC, A second oil supply groove G2 communicating with the second oil supply groove H2 is formed.

Here, the oil supply groove G2 may be formed to be long or inclined in the vertical direction. An end of the lower end of the oil supply groove G2 adjacent to the axial end of the orbiting wrap 372 prevents oil from flowing into the oil supply groove G2 from flowing down, So as to block the inflow of the gas.

The upper end of the oil supply groove G2 is preferably formed in a closed structure to prevent oil supplied to the oil supply groove G2 from excessively flowing out to the intermediate pressure region. To this end, the axial length of the oil supply groove G2 may be shorter than the axial length of the eccentric part EC.

When the line connecting the center of the eccentric portion with the center of the eccentric portion is referred to as the axis of the axis of the oil supply hole H2 or the oil supply groove G2 as described above, Lt; RTI ID = 0.0 > to 270 < / RTI >

It is to be understood that the above-described embodiments are to be considered in all respects as illustrative and not restrictive, and the scope of the present invention will be indicated by the appended claims rather than by the foregoing detailed description.

H1: first lubrication hole H2: second lubrication hole
H3: Third refueling hole H4: Fourth refueling hole
G1: first oil supply groove G2: second oil supply groove
G3: Third oil supply groove 100: Scroll compressor
200: compression section 210: casing
220: drive motor 226:
MB: Main bearing part SB: Sub bearing part
EC: Eccentric part 230: Main frame
240: orbiting scroll 241: orbiting wrap
250: fixed scroll 251: stationary wrap
270: Discharge cover 271: Oil feeder

Claims (15)

A casing in which oil is stored in a lower oil storage space;
A driving motor provided inside the casing;
A main frame coupled to the casing and disposed on one side of the driving motor;
A fixed scroll fixed to one side of the frame;
A rotary shaft coupled to the drive motor and having an oil supply passage for guiding the oil contained in the oil storage space of the casing upward and an eccentric portion eccentrically coupled to the orbiting scroll;
A revolving scroll engaging with the fixed lap of the fixed scroll; and a rotary shaft engaging portion rotatably coupled to the eccentric portion and forming a compression chamber together with the revolving lap;
An oil supply hole passing through the eccentric portion; And
And an oil supply groove communicating with the oil supply hole and formed on an outer circumferential surface of the eccentric portion and having upper and lower ends closed
Scroll compressor.
The method according to claim 1,
The rotating shaft
A main bearing portion supported on the frame,
And a sub-bearing portion supported by the fixed scroll,
The eccentric portion is disposed between the main bearing portion and the sub bearing portion
Scroll compressor.
3. The method of claim 2,
The rotating shaft
An oil supply hole passing through an outer circumferential surface of the main bearing portion; and an oil supply groove formed in an upper and lower direction on an outer circumferential surface of the main bearing portion
Scroll compressor.
The method of claim 3,
The rotating shaft
And an oil supply hole passing through an outer peripheral surface of the sub bearing portion
Scroll compressor
A casing in which oil is stored in a lower oil storage space;
A driving motor provided inside the casing;
A main frame coupled to the casing and disposed on one side of the driving motor;
A fixed scroll fixed to one side of the main frame;
A revolving scroll disposed between the frame and the fixed scroll and pivotally moving with respect to the fixed scroll, the revolving scroll including a revolving lap that engages with the fixed lap of the fixed scroll to form a compression chamber;
A rotary shaft coupled to the drive motor and having an oil supply passage for guiding the oil contained in the oil storage space of the casing to an upper side and an eccentric portion eccentrically coupled to the orbiting scroll;
An oil supply hole passing through the eccentric portion;
An oil supply groove formed on an outer peripheral surface of the eccentric portion so as to communicate with the oil supply hole; And
And a shut-off member for shutting off oil from both ends in the axial direction of the oil supply groove
Scroll compressor.
6. The method of claim 5,
The position of the eccentric portion on the rotation axis overlaps with the orbiting wrap
Scroll compressor.
6. The method of claim 5,
The rotating shaft
A main bearing portion supported on the frame,
A sub-bearing portion supported by the fixed scroll,
An eccentric portion disposed between the main bearing portion and the sub bearing portion,
A first small-diameter portion disposed between the main bearing portion and the eccentric portion and having an outer diameter smaller than the outer diameter of the eccentric portion,
And a second small-diameter portion disposed between the eccentric portion and the sub-bearing portion and having an outer diameter smaller than the outer diameter of the sub-bearing portion
Scroll compressor.
8. The method of claim 7,
The rotating shaft
And an oil supply hole passing through the main bearing portion or the first small diameter portion
Scroll compressor
A casing in which oil is stored in a lower oil storage space;
A driving motor provided inside the casing;
A frame internally coupled to the casing and disposed at one side of the driving motor;
A fixed scroll fixed to one side of the frame;
A revolving scroll disposed between the frame and the fixed scroll and pivotally moving with respect to the fixed scroll, the revolving scroll including a revolving lap that engages with the fixed lap of the fixed scroll to form a compression chamber; And
And a rotation shaft coupled to the drive motor and having an oil supply passage for guiding the oil contained in the oil storage space of the casing upward, and an eccentric portion eccentrically coupled to the orbiting scroll,
Wherein the rotary shaft coupling portion of the orbiting scroll to which the eccentric portion is coupled is provided with an oil supply groove on the inner surface thereof and the oil supply hole is connected to the oil supply passage in an area where the eccentric portion overlaps with the oil supply groove
Scroll compressor.
10. The method of claim 9,
The rotating shaft-
And a sealing section that is in close contact with the eccentric portion at both axial ends of the oil supply groove
Scroll compressor.
11. The method of claim 10,
The sealing section
An apparatus comprising: an annular blocking member; and an annular groove
Scroll compressor.
10. The method of claim 9,
The rotating shaft
A main bearing portion supported on the frame,
And a sub-bearing portion supported by the fixed scroll
The eccentric portion is disposed between the main bearing portion and the sub bearing portion
Scroll compressor.
13. The method of claim 12,
The rotating shaft
An oil supply hole communicating with the oil supply passage through the outer peripheral surface of the main bearing portion;
And an oil supply hole passing through an outer peripheral surface of the sub bearing portion and communicating with the oil supply passage
Scroll compressor
A casing in which oil is stored in a lower oil storage space;
A driving motor provided inside the casing;
A frame internally coupled to the casing and disposed at one side of the driving motor;
A fixed scroll fixed to one side of the frame;
A revolving scroll disposed between the frame and the fixed scroll and pivotally moving with respect to the fixed scroll, the revolving scroll including a revolving lap that engages with the fixed lap of the fixed scroll to form a compression chamber; And
A rotating shaft coupled to the driving motor and having a main bearing portion supported by the frame, a sub bearing portion supported by the fixed scroll, and an eccentric portion eccentrically coupled to the orbiting scroll;
An oil feeder coupled to a lower end of the sub bearing portion to pump the oil stored in the oil storage space;
An oil supply passage for guiding the oil pumped by the oil feeder from the inside to the upper side of the rotating shaft;
An oil supply hole passing through the eccentric portion and connected to the oil supply passage;
An oil supply groove formed on an outer peripheral surface of the eccentric portion so as to cross the oil supply hole; And
And a blocking portion formed at both ends of the oil supply groove on an outer circumferential surface of the eccentric portion and closely attached to a rotary shaft coupling portion provided on the orbiting scroll
Scroll compressor.
15. The method of claim 14,
The rotating shaft
An oil supply hole communicating with the oil supply passage through the outer peripheral surface of the main bearing portion;
And an oil supply hole passing through an outer peripheral surface of the sub bearing portion and communicating with the oil supply passage
Scroll compressor.

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