KR102330187B1 - Compressor having spiral oil groove structure - Google Patents

Abstract

The present invention relates to a compressor having an oil groove formed on an outer peripheral surface of a rotating shaft to be inclined in a direction opposite to the rotation of the rotating shaft in order to supply sufficient oil to the main bearing. The compressor may supply sufficient oil to the main bearing part by including an oil supply passage for guiding the oil contained in the oil storage space of the casing upward and an oil hole penetrating from the oil supply passage to the outer circumferential surface of the rotating shaft. In addition, an oil groove having one end connected to the oil hole and extending from the oil hole to the oil storage space in a direction opposite to the rotation of the rotation shaft is provided, so that oil can be uniformly supplied to the entire outer circumferential surface of the main bearing unit.

Description

Compressor with spiral oil groove structure {COMPRESSOR HAVING SPIRAL OIL GROOVE STRUCTURE}

The present invention relates to a compressor provided with an oil groove inclined in the direction opposite to the rotation of the rotation shaft on the outer circumferential surface of the rotation shaft in order to supply sufficient oil to the main bearing.

In general, a compressor is applied to a vapor compression type refrigeration cycle (hereinafter, abbreviated as a refrigeration cycle) such as a refrigerator or an air conditioner.

The compressor may be classified into a reciprocating type, a rotary type, a scroll type, etc. according to a method of compressing the refrigerant.

Among them, the scroll compressor is a compressor in which a compression chamber is formed between the fixed lap of the fixed scroll and the orbiting lap of the orbiting scroll by engaging the orbiting scroll with the fixed scroll fixed in the inner space of the sealed container and rotating.

Scroll compressors are widely used for refrigerant compression in air conditioners because of their advantages in that they can obtain a relatively high compression ratio compared to other types of compressors, and achieve stable torque by smoothly connecting refrigerant suction, compression, and discharge strokes.

The scroll compressor may be classified into an upper compression type or a lower compression type according to the positions of the driving motor and the compression unit. The upper compression type is a method in which the compression unit is located above the driving motor, and the lower compression type is a method in which the compression unit is located below the driving motor.

Here, in the case of the lower compression scroll compressor, a relatively uniform oil supply is possible because the distance between the oil storage space and the compression unit is short, but it may be structurally difficult to supply oil.

Therefore, it is necessary to improve the oil supply structure for the structurally difficult to supply oil (eg, the main bearing part of the rotating shaft).
Background art of the present invention is published in Korean Patent Publication No. 10-2234708 (registered on March 26, 2021, title of invention: scroll compressor).

SUMMARY OF THE INVENTION It is an object of the present invention to provide a compressor including an oil groove structure capable of uniformly supplying oil guided upward in an oil storage space to the entire outer circumferential surface of a main bearing part.

Another object of the present invention is to provide a compressor including an oil groove structure capable of rapidly moving oil guided upward in an oil storage space into a compression unit by using a rotational force of a rotating shaft.

The objects of the present invention are not limited to the objects mentioned above. In addition, other objects and advantages of the present invention not mentioned may be understood by the following description, and will be more clearly understood by the examples of the present invention. Moreover, it will be readily apparent that the objects and advantages of the present invention may be realized by the means and combinations thereof indicated in the claims.

The compressor according to the present invention has an oil supply passage for guiding the oil contained in the oil storage space of the casing upward, and an oil hole penetrating from the oil supply passage to the outer circumferential surface of the main bearing portion, thereby smoothly supplying oil to the main bearing portion. . In addition, by further comprising an oil groove having one end connected to the oil hole and extending from the oil hole to the oil storage space in a direction opposite to the rotation of the rotation shaft, oil can be uniformly supplied to the entire outer circumferential surface of the main bearing part.

In addition, the compressor according to the present invention has an oil groove formed in a direction of an inertia force according to the rotational force of the rotating shaft and a resultant force for gravity acting on the oil, so that the oil discharged through the oil hole can be quickly moved into the compression unit.

The compressor according to the present invention can prevent wear of the main bearing part by smoothly supplying oil to the entire outer circumferential surface of the main bearing part through the oil groove extending toward the oil storage space in the direction opposite to the rotation of the rotating shaft. In addition, the reliability of the main bearing part can be secured by preventing wear of the main bearing part.

In addition, the compressor according to the present invention is provided with an oil groove formed in the direction of the resultant force to the inertia force against the rotational force of the rotating shaft and the gravity acting on the oil, so that the oil on the oil groove can be quickly moved into the compression unit. Through this, it is possible to provide sufficient oil in the compression part, and it is possible to improve the operation efficiency of the compression part.

In addition to the above-described effects, the specific effects of the present invention will be described together while describing specific details for carrying out the invention below.

1 is a cross-sectional view illustrating a compressor according to an embodiment of the present invention.
Figure 2 is a schematic diagram for explaining the oil supply structure of the compressor of Figure 1.
3 and 4 are views for explaining an example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 .
5 and 6 are views for explaining an oil groove of the compressor of FIG. 1 .
7 is a cross-sectional view taken along section AA of FIG. 6 .
FIG. 8 is a view for explaining another example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 .
FIG. 9 is a view for explaining another example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 .

Hereinafter, preferred embodiments according to the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same reference numerals are used to refer to the same or similar components.

Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to FIGS. 1 to 7 .

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

1, the compressor according to the embodiment of the present invention has a casing 210 having an inner space, a drive motor 220 provided in the upper portion of the inner space, and a compression unit disposed at the lower end of the drive motor 220 ( 290 ) and the rotation shaft 100 for transmitting the driving force of the driving motor 220 to the compression unit 290 may be included.

Here, the inner space of the casing 210 includes a first space V1 above the drive motor 220, a second space V2 between the drive motor 220 and the compression unit 290, and a discharge cover ( It may be divided into a third space V3 partitioned by the 270 and a storage space V4 below the compression unit 290 .

The casing 210 may have a cylindrical shape, for example, and thus the casing 210 may include a cylindrical shell 211 .

In addition, the upper shell 212 may be installed on the upper portion of the cylindrical shell 211 , and the lower shell 214 may be installed on the lower portion of the cylindrical shell 211 . The upper and lower shells 212 and 214 may be coupled to the cylindrical shell 211 by welding, for example, to form an inner space.

Here, a refrigerant discharge pipe 216 may be installed in the upper shell 212 , and the refrigerant discharge pipe 216 is discharged from the compression unit 290 into the second space V2 and the first space V1 . It is a passage through which the compressed refrigerant is discharged to the outside.

For reference, an oil separator (not shown) that separates oil mixed in the discharged refrigerant may be connected to the refrigerant discharge pipe 216 .

The lower shell 214 may form a storage space V4 for storing oil.

The oil storage space V4 may function as an oil chamber for supplying oil to the compression unit 290 so that the compressor may operate smoothly.

In addition, a refrigerant suction pipe 218 that is a passage through which the refrigerant to be compressed is introduced may be installed on the side of the cylindrical shell 211 .

The refrigerant suction pipe 218 may be installed to pass through the compression chamber S1 along the side surface of the fixed scroll 250 .

The driving motor 220 may be installed on the inner side of the casing 210 .

Specifically, the driving motor 220 may include a stator 222 and a rotor 224 .

The stator 222 may be, for example, cylindrical, and may be fixed to the casing 210 . A plurality of slots (not shown) are formed on the inner peripheral surface of the stator 222 in the circumferential direction so that the coil 222a is wound. In addition, a refrigerant passage groove 212a may be formed on the outer circumferential surface of the stator 222 to allow the refrigerant or oil discharged from the compression unit 290 to pass through being cut in a D-cut shape.

The rotor 224 may be coupled to the inside of the stator 222 and generate rotational power. That is, the rotor 224 may rotate with the rotation shaft 100 by press-fitting the rotation shaft 100 to the center thereof. The rotational power generated by the rotor 224 is transmitted to the compression unit 290 through the rotation shaft 100 .

The compression unit 290 may include the main frame 230 , the fixed scroll 250 , the orbiting scroll 240 , and the discharge cover 270 .

For reference, the compression unit 290 may further include an Oldham's ring 150 . The Oldham ring 150 may be installed between the orbiting scroll 240 and the main frame 230 . In addition, the Oldham ring 150 prevents the orbiting scroll 240 from rotating while enabling the orbiting scroll 240 to pivot on the fixed scroll 250 .

The main frame 230 may be provided under the driving motor 220 and form an upper portion of the compression unit 290 .

The main frame 230 includes a frame head plate part (hereinafter, a first end plate part) 232 having a substantially circular shape, and a frame bearing part (hereinafter, provided in the center of the first head plate part 232) through which the rotation shaft 100 passes. A first bearing portion) 232a and a frame sidewall portion (hereinafter, referred to as a first sidewall portion) 231 protruding downward from the outer periphery of the first end plate portion 232 may be provided.

The first sidewall portion 231 may have an outer peripheral portion in contact with an inner peripheral surface of the cylindrical shell 211 , and a lower end portion in contact with an upper portion of a fixed scroll sidewall portion 255 , which will be described later.

A frame discharge hole (hereinafter, referred to as a first discharge hole) 231a penetrating the inside of the first sidewall portion 231 in the axial direction to form a refrigerant passage may be provided in the first side wall portion 231 . The first discharge hole 231a may have an inlet connected to an outlet of a fixed scroll discharge hole 256b, which will be described later, and an outlet connected to the second space V2.

The first bearing part 232a may be formed to protrude from the upper surface of the first head plate part 232 toward the driving motor 220 . In addition, a first bearing part may be formed in the first bearing part 232a so that the main bearing part MB of the rotation shaft 100, which will be described later, is penetrated and supported.

That is, in the center of the main frame 230 , the first bearing portion 232a in which the main bearing portion MB of the rotary shaft 100 constituting the first bearing portion is rotatably inserted and supported may be formed through in the axial direction. .

An oil pocket 232b for collecting oil discharged between the first bearing part 232a and the rotation shaft 100 may be formed on an upper surface of the first end plate part 232 . The oil pocket 232b may be engraved on the upper surface of the first end plate 232 and may be formed in an annular shape along the outer circumferential surface of the first bearing portion 232a.

A back pressure chamber S2 may be formed on the bottom surface of the main frame 230 to form a space together with the fixed scroll 250 and the orbiting scroll 240 to support the orbiting scroll 240 by the pressure of the space.

For reference, the back pressure chamber S2 may include an intermediate pressure region (ie, an intermediate pressure chamber), and the oil supply passage 110 provided in the rotary shaft 100 has a high pressure region having a higher pressure than that of the back pressure chamber S2 . may include

A back pressure seal 280 may be provided between the main frame 230 and the orbiting scroll 240 to separate the high pressure region and the intermediate pressure region, and the back pressure seal 280 is, for example, a sealing member. can play a role

In addition, the main frame 230 may be combined with the fixed scroll 250 to form a space in which the orbiting scroll 240 can be installed so as to be pivotable. That is, this structure may be a structure surrounding the rotation shaft 100 so that rotational power can be transmitted to the compression unit 290 through the rotation shaft 100 .

A fixed scroll 250 constituting the first scroll may be coupled to the bottom surface of the main frame 230 .

Specifically, the fixed scroll 250 may be provided under the main frame 230 .

In addition, the fixed scroll 250 includes a fixed scroll end plate part (second end plate part) 254 having a substantially circular shape, and a fixed scroll side wall part (hereinafter, referred to as a second side wall) protruding upward from the outer periphery of the second end plate part 254 . part) 255 , a fixing wrap 251 protruding from the upper surface of the second end plate 254 and engaging with the orbiting wrap 241 of the orbiting scroll 240 to be described later to form a compression chamber S1 , and a second A fixed scroll bearing portion (hereinafter, referred to as a second bearing portion) 252 formed in the center of the rear surface of the head plate portion 254 and through which the rotation shaft 100 passes may be provided.

A discharge port 253 for guiding the compressed refrigerant from the compression chamber S1 to the inner space of the discharge cover 270 may be formed in the second end plate 254 . The position of the discharge port 253 may be arbitrarily set in consideration of a required discharge pressure and the like.

Here, as the discharge port 253 is formed toward the lower shell 214, a fixed scroll discharge hole 256b, which will be described later, is provided on the lower surface of the fixed scroll 250 to receive the discharged refrigerant and prevent the refrigerant from mixing with oil. A discharge cover 270 for guiding the . The discharge cover 270 may be sealingly coupled to the bottom surface of the fixed scroll 250 so as to separate the refrigerant discharge passage and the storage space V4.

In addition, in the discharge cover 270 , the oil feeder 271 coupled to the sub bearing part SB of the rotary shaft 100 constituting the second bearing part and immersed in the oil storage space V4 of the casing 210 passes through a through hole. 276 may be formed.

Meanwhile, in the second side wall part 255 , a fixed scroll discharge hole (hereinafter, referred to as a second discharge hole) that penetrates the inside of the second side wall part 255 in the axial direction and forms a refrigerant passage together with the first discharge hole 231a ) (256b) may be provided.

The second discharge hole 256b may be formed to correspond to the first discharge hole 231a, the inlet may be connected to the inner space of the discharge cover 270, and the outlet may be connected to the inlet of the first discharge hole 231a. .

Here, the second discharge hole 256b and the first discharge hole 231a are formed so that the refrigerant discharged from the compression chamber S1 to the inner space of the discharge cover 270 is guided to the second space V2. The third space V3 and the second space V2 may be connected.

In addition, the refrigerant suction pipe 218 may be installed in the second side wall portion 255 to be connected to the suction side of the compression chamber S1 . Also, the refrigerant suction pipe 218 may be installed to be spaced apart from the second discharge hole 256b.

The second bearing part 252 may be formed to protrude from the lower surface of the second end plate part 254 toward the oil storage space V4.

In addition, the second bearing part 252 may be provided with a second bearing part so that the sub bearing part SB of the rotation shaft 100 is inserted and supported.

In addition, the lower end of the second bearing part 252 may be bent toward the center of the shaft to form a thrust bearing surface by supporting the lower end of the sub bearing part SB of the rotation shaft 100 .

An orbiting scroll 240 forming a second scroll may be installed between the main frame 230 and the fixed scroll 250 .

Specifically, the orbiting scroll 240 may be coupled to the rotation shaft 100 to form two pairs of compression chambers S1 between the fixed scroll 250 and the fixed scroll 250 while rotating.

In addition, the orbiting scroll 240 has a substantially circular orbiting scroll end plate part (hereinafter, referred to as a third end plate part) 245 , and an orbiting wrap protruding from the lower surface of the third end plate part 245 and engaged with the fixed wrap 251 . 241 and a rotation shaft coupling part 242 provided in the center of the third head plate part 245 and rotatably coupled to the eccentric part EC of the rotation shaft 100 may be included.

In the case of the orbiting scroll 240 , the outer periphery of the third end plate 245 is positioned at the upper end of the second side wall 255 , and the lower end of the orbiting wrap 241 is in close contact with the upper surface of the second end plate 254 . , may be supported on the fixed scroll 250 .

For reference, a pocket groove 180 for guiding oil discharged through oil holes H1 , H2 , and H3 to be described later to the intermediate pressure chamber may be formed on the upper surface of the orbiting scroll 240 .

Specifically, the pocket groove 180 may be engraved on the upper surface of the third end plate 245 . That is, the pocket groove 180 may be formed on the upper surface of the third end plate 245 between the back pressure seal 280 and the rotation shaft 100 .

In addition, as shown in the drawing, the pocket groove 180 may be formed one by one on each side of the rotation shaft 100 , or a plurality of pocket grooves 180 may be formed on either side of the rotation shaft 100 .

When a plurality of pocket grooves 180 are formed, the plurality of pocket grooves may be formed to be spaced apart from each other by a predetermined distance on the upper surface of the third end plate 245 between the back pressure seal 280 and the rotation shaft 100 .

Also, the pocket groove 180 may be formed in an annular shape on the upper surface of the third end plate 245 between the back pressure seal 280 and the rotation shaft 100 , centering on the rotation shaft 100 .

The outer periphery of the rotating shaft coupling portion 242 is connected to the orbital wrap 241 and serves to form a compression chamber S1 together with the fixed wrap 251 during the compression process.

For reference, the fixing wrap 251 and the orbiting wrap 241 may be formed in an involute shape, but may be formed in various other shapes.

Here, the involute shape means a curve corresponding to the trajectory drawn by the end of the yarn when the yarn wound around the base circle having an arbitrary radius is unwound.

In addition, the eccentric portion EC of the rotation shaft 100 may be inserted into the rotation shaft coupling portion 242 . The eccentric portion EC inserted into the rotating shaft coupling portion 242 may overlap the orbital wrap 241 or the fixed wrap 251 in the radial direction of the compressor.

Here, the radial direction may mean a direction (ie, left-right direction) orthogonal to the axial direction (ie, up-and-down direction), and more specifically, the radial direction may mean a direction from the outside to the inside of the rotation shaft. .

As described above, when the eccentric portion EC of the rotary shaft 100 penetrates through the third head plate portion 245 and overlaps with the orbital wrap 241 in a radial direction, the repulsive force and compressive force of the refrigerant are applied to the third head plate portion 245 . ) as a reference, they may be partially offset from each other while being applied to the same plane.

In addition, the rotating shaft 100 is coupled to the driving motor 220 , and may include an oil supply passage 110 for guiding oil contained in the oil storage space V4 of the casing 210 upward.

Specifically, the rotation shaft 100 is coupled to the upper portion of the press-fitted center of the rotor 224, the lower portion is coupled to the compression unit 290 may be supported in the radial direction.

Accordingly, the rotating shaft 100 may transmit the rotational force of the driving motor 220 to the orbiting scroll 240 of the compression unit 290 . In addition, through this, the orbiting scroll 240 eccentrically coupled to the rotating shaft 100 performs a pivoting motion with respect to the fixed scroll 250 .

A main bearing portion MB may be formed at a lower portion of the rotation shaft 100 to be inserted into the first bearing portion 232a of the main frame 230 to be radially supported. Also, a sub bearing part SB may be formed at a lower portion of the main bearing part MB to be inserted into the second bearing part 252 of the fixed scroll 250 and supported in a radial direction. In addition, an eccentric part EC may be formed between the main bearing part MB and the sub bearing part SB to be inserted into and coupled to the rotation shaft coupling part 242 of the orbiting scroll 240 .

The main bearing part MB and the sub bearing part SB are formed on a coaxial line to have the same axial center, and the eccentric part EC is radial with respect to the main bearing part MB or the sub bearing part SB. It can be formed eccentrically.

For reference, the eccentric part EC may have an outer diameter smaller than the outer diameter of the main bearing part MB and larger than the outer diameter of the sub bearing part SB. In this case, it may be advantageous to couple the rotation shaft 100 through each of the bearing parts 232a and 252 and the rotation shaft coupling part 242 .

On the other hand, the eccentric part EC may not be integrally formed with the rotation shaft 100 but may be formed using a separate bearing. In this case, the rotation shaft 100 is inserted into each of the bearing portions 232a and 252 and the rotation shaft coupling portion 242 without being formed to be smaller than the outer diameter of the eccentric portion EC. can

In addition, an oil supply flow path 110 for supplying the oil of the oil storage space V4 to the outer peripheral surface of each bearing part MB and SB and the outer peripheral surface of the eccentric part EC may be formed in the rotation shaft 100 . . In addition, oil holes H1 , H2 , and H3 penetrating from the oil supply passage 110 to the outer circumferential surface may be formed in the bearing portions and the eccentric portions MB, SB, and EC of the rotation shaft 100 .

Specifically, the first oil hole H1 may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the main bearing part MB.

In addition, a first oil groove (G1 in FIG. 2 ) of an oblique or spiral (eg, spiral shape) having one end connected to the first oil hole H1 may be formed on the outer circumferential surface of the main bearing part MB. .

Specifically, one end of the first oil groove (G1 in FIG. 2 ) is formed to be connected to the first oil hole H1 , so that some of the oil discharged from the first oil hole H1 is transferred to the first oil groove ( FIG. 2 ). It can be efficiently supplied to the outer peripheral surface of the main bearing part MB along the G1).

That is, some of the oil discharged from the first oil hole H1 flows along the first oil groove (G1 of FIG. 2 ) and may be supplied to the upper, lower, left, and right sides of the outer peripheral surface of the main bearing part MB.

For reference, the remaining oil discharged from the first oil hole H1 may be directly supplied to the upper, lower, left, and right sides of the outer peripheral surface of the main bearing unit MB with the first oil hole H1 as the center.

In this case, the first oil groove (G1 in FIG. 2 ) may be formed to be inclined in a direction opposite to the rotation of the rotation shaft 100 . A detailed description thereof will be provided later.

Meanwhile, the second oil hole H2 may be formed to penetrate the outer circumferential surface of the eccentric part EC.

In addition, a second oil groove (G2 in FIG. 2 ) may be formed on the outer peripheral surface of the eccentric part EC to be connected to the second oil hole H2 and extend in the vertical direction.

Specifically, as the second oil hole H2 is formed in the center of the second oil groove (G2 in FIG. 2 ), some of the oil discharged from the second oil hole H2 is partially transferred to the second oil groove (G2 in FIG. 2 ). ) along the outer peripheral surface of the eccentric (EC) can be efficiently supplied. That is, some of the oil discharged from the second oil hole H2 flows along the second oil groove (G2 of FIG. 2 ) and may be supplied to the upper, lower, left, and right sides of the outer peripheral surface of the eccentric part EC.

For reference, the remaining oil discharged from the second oil hole H2 may be directly supplied to the top, bottom, left, and right sides of the outer peripheral surface of the eccentric part 226d with the second oil hole H2 as the center.

Also, the second oil groove (G2 in FIG. 2 ) may be formed straight in the vertical direction (ie, the longitudinal direction) as shown in the drawing, but may be inclined or spirally formed along the longitudinal direction in some cases.

Finally, the third oil hole H3 may be formed to penetrate the outer peripheral surface of the sub bearing part SB.

As a result, the oil guided upward through the oil supply passage 110 may be discharged through the first oil hole H1 to be supplied to the outer peripheral surface of the main bearing part MB as a whole.

In addition, the oil guided upward through the oil supply passage 110 may be discharged through the second oil hole H2 and supplied to the outer circumferential surface of the eccentric part EC as a whole.

In addition, the oil guided upward through the oil supply flow path 110 is discharged through the third oil hole H3 to the outer peripheral surface of the sub bearing part SB or between the orbiting scroll 240 and the fixed scroll 250 . can be supplied to

In addition, an oil feeder 271 for pumping oil filled in the oil storage space V4 may be coupled to the lower end of the rotation shaft 100 , that is, the lower end of the sub bearing part SB.

The oil feeder 271 includes an oil supply pipe 273 that is inserted into and coupled to the oil supply passage 110 of the rotary shaft 100, and an oil suction member 274 that is inserted into the oil supply pipe 273 to suck oil. can be done

Here, the oil supply pipe 273 may be installed to pass through the through hole 276 of the discharge cover 270 to be submerged in the oil storage space V4, and the oil suction member 274 may function as a propeller.

In addition, although not shown in the drawings, a trochoid pump (not shown) is coupled to the sub bearing part SB to forcibly pump the oil filled in the storage space V4 to the upper part instead of the oil feeder 271 . may be

In addition, although not shown in the drawings, the compressor according to the embodiment of the present invention includes a first sealing member (not shown) for sealing the gap between the upper end of the main bearing unit MB and the upper end of the main frame 230 , and A second sealing member (not shown) for sealing a gap between the lower end of the sub bearing part SB and the lower end of the fixed scroll 250 may be further included.

For reference, it is possible to prevent oil from flowing out of the compression part 290 along the bearing surface (ie, the outer peripheral surface of the bearing part) through these first and second sealing members, and through this, the differential pressure in the compression part 290 can be prevented. It is possible to realize the oil supply structure and prevent the reverse flow of the refrigerant.

A balance weight 227 for suppressing noise and vibration may be coupled to the rotor 224 or the rotation shaft 100 .

For reference, the balance weight 227 may be provided between the driving motor 220 and the compression unit 290 , that is, in the second space V2 .

Next, an operation process of the compressor according to the embodiment of the present invention will be described as follows.

When power is applied to the driving motor 220 to generate rotational force, the rotation shaft 100 coupled to the rotor 224 of the driving motor 220 rotates. Then, the orbiting scroll 240 eccentrically coupled to the rotating shaft 100 rotates with respect to the fixed scroll 250 to form a compression chamber S1 between the orbiting wrap 241 and the fixed wrap 251 . The compression chamber S1 may be continuously formed in several stages while gradually decreasing in volume in the central direction.

Then, the refrigerant supplied through the refrigerant suction pipe 218 from the outside of the casing 210 may be directly introduced into the compression chamber (S1). This refrigerant is compressed while moving in the direction of the discharge chamber of the compression chamber S1 by the orbiting motion of the orbiting scroll 240 , and then from the discharge chamber to the third space V3 through the discharge port 253 of the fixed scroll 250 . can be ejected.

Thereafter, the compressed refrigerant discharged to the third space V3 is discharged into the inner space of the casing 210 through the second discharge hole 256b and the first discharge hole 231a, and then the refrigerant discharge pipe 216 . A series of processes of being discharged to the outside of the casing 210 are repeated.

Hereinafter, an example of the oil supply structure of the compressor of FIG. 1 will be described with reference to FIG. 2 .

Figure 2 is a schematic diagram for explaining the oil supply structure of the compressor of Figure 1.

For reference, FIG. 2 shows the oil flow according to the differential pressure refueling structure.

Specifically, the oil stored in the oil storage space (V4 in FIG. 1 ) may be guided (ie, moved or supplied) upward through the oil supply passage ( 110 in FIG. 1 ) of the rotary shaft 100 .

In addition, as shown in FIG. 2 , the oil guided upward through the oil supply passage ( 110 in FIG. 1 ) is discharged through the first oil hole H1 and supplied to the outer peripheral surface of the main bearing part MB as a whole. can be

In addition, the oil guided upward through the oil supply flow path 110 in FIG. 1 may be discharged through the second oil hole H2 and supplied to the outer peripheral surface of the eccentric part EC as a whole.

In addition, the oil guided upward through the oil supply flow path 110 (in FIG. 1 ) is discharged through the third oil hole H3 to the outer peripheral surface of the sub bearing part SB or the orbiting scroll 240 and the fixed scroll 250 . ) can be supplied between

As described above, the oil contained in the oil storage space V4 is guided upward through the rotation shaft 100 and is smoothly supplied to the bearing portion, that is, the bearing surface through the plurality of oil holes H1, H2, H3, so that the bearing portion wears out. can be prevented.

Also, the oil discharged through the plurality of oil holes H1 , H2 , and H3 may form an oil film between the fixed scroll 250 and the orbiting scroll 240 to maintain an airtight state.

In addition, the oil discharged through the plurality of oil holes H1 , H2 , and H3 may absorb friction heat generated in the friction part to lower the temperature of the high-temperature compression part 290 .

On the other hand, the high-pressure oil guided upward through the oil supply passage 110 (in FIG. 1 ) is discharged through the first oil hole H1 and guided by the first oil groove G1 to the orbiting scroll 240 . It can be supplied on the upper surface of Also, the oil supplied to the upper surface of the orbiting scroll 240 may be guided to the intermediate pressure chamber S2 through the pocket groove 180 .

For reference, oil discharged through the first oil hole H1 as well as the second oil hole H2 or the third oil hole H3 may be supplied to the pocket groove 180 .

In this case, the first oil groove G1 may provide sufficient oil to the pocket groove 180 .

Specifically, the first oil groove G1 may extend toward the oil storage space V4 in a direction opposite to the rotation of the rotation shaft 100 . The first oil groove G1 may rapidly move the oil discharged from the first oil hole H1 downward to provide a sufficient amount of oil into the compression unit 290 .

At this time, the first oil groove G1 has an inertia force vector generated by the rotational force of the rotary shaft 100 acting on the position of the first oil hole H1 and gravity acting on the oil discharged from the first oil hole H1 . It may be formed in the same direction as the direction of the resultant force of the vector.

Through this, the direction of the force received by the oil discharged from the first oil hole H1 coincides with the direction in which the first oil groove G1 extends, so that the first oil groove G1 quickly orbits the supplied oil. It can be guided to the upper surface of (240).

Subsequently, the oil supplied to the upper surface of the orbiting scroll 240 may be guided to the intermediate pressure chamber S2 through the pocket groove 180 .

Subsequently, the oil guided to the intermediate pressure chamber S2 may be supplied to the thrust surface of the Oldham ring 150 and the fixed scroll 250 installed between the orbiting scroll 240 and the main frame 230 .

That is, the oil introduced into the intermediate pressure chamber S2 may be sufficiently provided to the thrust surface of the fixed scroll 250 and the Oldham ring 150 .

Through this, it is possible to reduce wear of the thrust surface of the fixed scroll 250 and the Oldham ring 150 .

Subsequently, the oil guided to the intermediate pressure chamber S2 may be guided to a differential pressure oil supply passage (not shown) provided in the fixed scroll 250 .

Specifically, the fixed scroll 250 of the compressor may further include a differential pressure oil supply flow path (not shown) for guiding the oil guided to the intermediate pressure chamber (ie, S2 ) to the compression chamber S1 . Accordingly, the oil contained in the oil storage space may be smoothly supplied to the compression chamber S1 through the pocket groove 180 and the differential pressure oil supply passage (not shown).

In addition, by smoothly supplying oil to the compression chamber S1 , wear due to friction between the orbiting scroll 240 and the fixed scroll 250 may be reduced, and thus, compression efficiency may be improved.

In addition, the oil supplied to the compression chamber S1 may form an oil film between the fixed scroll 250 and the orbiting scroll 240 to maintain an airtight state.

Furthermore, the oil supplied to the compression chamber S1 may absorb and radiate heat generated during friction between the fixed scroll 250 and the orbiting scroll 240 .

Hereinafter, the plurality of oil holes H1 , H2 , H3 and the oil grooves G1 and G2 formed in the rotation shaft 190 will be described in detail.

3 and 4 are views for explaining an example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 .

3 and 4, an oil supply flow path for supplying the oil of the oil storage space V4 to the outer peripheral surface of each bearing part MB, SB and the outer peripheral surface of the eccentric part EC in the inside of the rotating shaft 100 ( 110) may be formed.

Oil holes H1 , H2 , and H3 penetrating from the oil supply passage 110 to the outer circumferential surface may be formed in the bearing portions and the eccentric portions MB, SB, and EC of the rotation shaft 100 .

Specifically, the oil holes H1 , H2 , and H3 may include a first oil hole H1 , a second oil hole H2 , and a third oil hole H3 .

First, the first oil hole H1 may be formed to pass through the outer circumferential surface of the main bearing part MB.

Specifically, the first oil hole H1 may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the main bearing part MB.

Also, the first oil hole H1 may be formed to pass through, for example, an upper portion of an outer circumferential surface of the main bearing part MB, but is not limited thereto. That is, it may be formed to penetrate the lower part of the outer peripheral surface of the main bearing part MB.

For reference, the first oil hole H1 may include a plurality of holes, unlike in the drawings.

In addition, when the first oil hole H1 includes a plurality of holes, each hole may be formed only on the upper or lower part of the outer peripheral surface of the main bearing part MB, and may be formed on the upper part and the lower part of the outer peripheral surface of the main bearing part MB. It may be respectively formed in the lower part.

However, for convenience of description, in the embodiment of the present invention, the first oil hole H1 will be described as an example including one hole.

Also, an oblique or spiral first oil groove G1 having one end connected to the first oil hole H1 may be formed on the outer circumferential surface of the main bearing part MB.

Specifically, one end of the first oil groove G1 is formed to be connected to the first oil hole H1, so that some of the oil discharged from the first oil hole H1 is main along the first oil groove G1. It can be efficiently supplied to the outer peripheral surface of the bearing portion (MB). That is, some of the oil discharged from the first oil hole H1 flows along the first oil groove G1 and may be supplied to the top, bottom, left, and right sides of the outer peripheral surface of the main bearing part MB.

For reference, the remaining oil discharged from the first oil hole H1 may be directly supplied to the upper, lower, left, and right sides of the outer peripheral surface of the main bearing unit MB with the first oil hole H1 as the center.

The first oil groove G1 may be inclined in a direction opposite to the rotation of the rotation shaft 100 .

That is, the first oil groove G1 may extend downward of the rotation shaft 100 in a direction opposite to the rotation. The first oil groove G1 may be formed by spirally or obliquely engraving on the outer circumferential surface of the main bearing part MB.

In this case, the first oil groove G1 may be formed such that one end is connected to the first oil hole H1 and the other end is connected to the lower surface of the main bearing part MB.

However, the present invention is not limited thereto, and unlike the drawings, one end of the first oil groove G1 passes through the first oil hole H1 to be connected to the upper surface of the main bearing unit MB. It may be formed by extending.

Also, the first oil groove G1 may include a plurality of grooves, unlike the one illustrated in the drawings.

For example, when the first oil groove G1 includes a plurality of grooves and the first oil hole H1 includes one hole, one end of each groove is connected to the first oil hole H1. can be formed.

Also, when the first oil groove G1 includes a plurality of grooves and the first oil hole H1 also includes a plurality of holes, one end of each groove may be formed to be connected to each hole one-to-one.

However, for convenience of description, in the embodiment of the present invention, the first oil groove G1 will be described as an example including one groove.

A first small diameter portion 104 may be formed between the main bearing portion MB and the eccentric portion EC. The first small diameter portion 104 may be spaced apart from the main bearing portion MB and the eccentric portion EC by a predetermined interval.

For reference, the first small diameter portion 104 may be provided to secure workability when the main bearing portion MB and the eccentric portion EC are formed through a grinding process. In addition, the first small-diameter portion 104 may be provided to secure a damping space for continuous supply of the oil guided upward through the rotation shaft 100 .

Although not clearly illustrated in the drawings, an additional oil hole (not shown) may be formed between the main bearing part MB and the eccentric part EC. In this case, an oil hole (not shown) may be formed in the first small-diameter portion 104 . That is, the oil hole (not shown) may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the first small-diameter portion 104 .

Meanwhile, the second oil hole H2 may be formed to penetrate the outer circumferential surface of the eccentric part EC.

Specifically, the second oil hole H2 may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the eccentric portion EC.

In addition, the second oil hole H2 may be formed to pass through, for example, a middle part of the outer peripheral surface of the eccentric part EC, but is not limited thereto.

That is, the second oil hole H2 may be formed to penetrate an upper portion or a lower portion of the outer peripheral surface of the eccentric portion EC.

For reference, the first direction extending from the center of the rotary shaft 100 to the outer circumferential surface in the first oil hole H1 is a second direction extending from the center of the rotary shaft 100 to the outer circumferential surface in the second oil hole H2 and may be different. However, the present invention is not limited thereto, and the first direction and the second direction may have an acute angle or an obtuse angle, or may be the same as each other.

Also, the second oil hole H2 may include a plurality of holes, unlike the one illustrated in the drawing. When the second oil hole H2 includes a plurality of holes, each hole may be formed only in a middle part of the outer circumferential surface of the eccentric part EC, and may be formed in upper and lower portions of the outer circumferential surface of the eccentric part EC, respectively. may be

However, for convenience of description, in the embodiment of the present invention, it will be described that the second oil hole H2 includes one hole.

Also, a second oil groove G2 may be formed on the outer circumferential surface of the eccentric portion EC to be connected to the second oil hole H2 and extend in the vertical direction.

Specifically, as the second oil hole H2 is formed in the center of the second oil groove G2, some of the oil discharged from the second oil hole H2 is partly eccentric along the second oil groove G2. EC) can be efficiently supplied to the outer peripheral surface. That is, some of the oil discharged from the second oil hole H2 flows along the second oil groove G2 and may be supplied to the upper, lower, left, and right sides of the outer peripheral surface of the eccentric part EC.

For reference, the remaining oil discharged from the second oil hole H2 may be directly supplied to the top, bottom, left, and right sides of the outer peripheral surface of the eccentric part 226d with the second oil hole H2 as the center.

Of course, the second oil hole H2 may be formed above or below the second oil groove G2.

Also, the second oil groove G2 may be formed straight in the vertical direction (ie, the longitudinal direction) as shown in the drawing, but may be inclined or spirally formed along the longitudinal direction in some cases.

For reference, the second oil groove G2 may include a plurality of grooves differently from that shown in the drawings.

For example, when the second oil groove G2 includes a plurality of grooves and the second oil hole H2 also includes a plurality of holes, each hole may be formed in the center of each groove.

However, for convenience of description, in the embodiment of the present invention, the second oil groove G2 will be described as an example including one groove.

Meanwhile, the second small diameter portion 106 may be formed between the eccentric portion EC and the sub bearing portion SB. The second small diameter portion 106 may be spaced apart from the eccentric portion EC and the sub bearing portion SB by a predetermined distance.

In this case, the height of the second small-diameter portion 106 may be the same as or different from the height of the first small-diameter portion 104 .

For reference, the second small-diameter portion 106 may be provided to secure workability when the eccentric portion EC and the sub-bearing portion SB are formed through a grinding process. In addition, the second small diameter portion 106 is also provided to secure a damping space for the continuous supply of the oil guided upward through the rotation shaft 100 .

Although not clearly illustrated in the drawings, an additional oil hole (not shown) may be formed between the eccentric part EC and the sub bearing part SB. In this case, an oil hole (not shown) may be formed in the second small-diameter portion 106 . That is, the oil hole (not shown) may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the second small-diameter portion 106 .

Finally, the third oil hole H3 may be formed on the sub bearing part SB.

Specifically, the third oil hole H3 may be formed to penetrate from the oil supply passage 110 to the outer circumferential surface of the sub bearing part SB.

Also, the third oil hole H3 may be formed to pass through, for example, a middle part of the outer peripheral surface of the sub bearing part SB. However, the present invention is not limited thereto, and the third oil hole H3 may be formed to penetrate the upper or lower portion of the outer peripheral surface of the sub bearing part SB.

For reference, the third direction extending from the center of the rotary shaft 100 to the outer circumferential surface in the third oil hole H3 is a second direction extending from the center of the rotary shaft 100 to the outer circumferential surface in the second oil hole H2 and may be different. However, the present invention is not limited thereto, and the third direction and the second direction may have an acute angle or an obtuse angle, or may be identical to each other.

In addition, the third oil hole H3 may include a plurality of holes, different from that illustrated in the drawings. When the third oil hole H3 includes a plurality of holes, each hole may be formed only in a middle portion of the outer peripheral surface of the sub bearing part SB, and may be formed in upper and lower portions of the outer peripheral surface of the sub bearing part SB, respectively. may be formed.

However, for convenience of description, in the embodiment of the present invention, it will be described that the third oil hole H3 includes one hole.

As a result, the oil guided upward through the oil supply passage 110 may be discharged through the first oil hole H1 to be supplied to the outer peripheral surface of the main bearing part MB as a whole.

In addition, the oil guided upward through the oil supply passage 110 may be guided along the first oil groove G1 to be supplied to the upper surface of the orbiting scroll 240 .

Also, the oil may be discharged through the second oil hole H2 and supplied to the outer peripheral surface of the eccentric part EC as a whole.

In addition, the oil guided upward through the oil supply flow path 110 is discharged through the third oil hole H3 to the outer peripheral surface of the sub bearing part SB or between the orbiting scroll 240 and the fixed scroll 250 . can be supplied.

5 and 6 are views for explaining an oil groove of the compressor of FIG. 1 . 7 is a cross-sectional view taken along section A-A of FIG. 6 . Hereinafter, content overlapping with the previously described content will be omitted, and differences will be mainly described.

Referring to FIG. 5 , the first oil groove G1 may be engraved on the outer circumferential surface of the main bearing part MB.

The first oil groove G1 may be formed to be inclined in a direction Wl opposite to the rotation direction Wr of the rotation shaft 100 toward a lower portion of the main bearing part MB.

Specifically, in the first oil groove G1, one end of the first oil groove G1 is connected to the first oil hole H1, and the other end of the first oil groove G1 is the lower surface of the main bearing part MB. It may be formed to be connected to.

The first oil groove G1 may be inclined to have a first angle θ1 from the center of the rotation shaft 100 . The first angle θ1 of the first oil groove G1 may have an acute angle (ie, a value between 0 degrees and 90 degrees).

In this case, the height Z1 of the first oil groove G1 may be smaller than the height Z2 of the main bearing part MB.

Similarly, the width X1 of the first oil groove G1 may be smaller than the diameter X2 of the main bearing part MB.

However, the present invention is not limited thereto, and when the first angle θ1 of the first oil groove G1 increases, the width X1 of the first oil groove G1 is the diameter of the main bearing part MB. It may be formed larger than (X2).

Additionally, unlike illustrated in the drawings, one end of the first oil groove G1 may be formed to extend upwardly through the first oil hole H1 to be connected to the upper surface of the main bearing part MB. In this case, the height Z1 of the first oil groove G1 may be equal to the height Z2 of the main bearing part MB.

6 and 7 , a plurality of forces may act on the oil guided by the first oil groove G1.

Specifically, the oil guided upward through the oil supply passage 110 by the differential pressure C between the oil storage space V4 and the compression unit 290 may be discharged to the outside through the first oil hole H1. . At this time, the oil guided upward by the differential pressure C is guided by the flow path 112 connecting the oil supply flow path 110 and the outer peripheral surface of the main bearing unit MB to move to the first oil hole H1 . can

The rotational force R of the rotating shaft 100 , the inertial force I acting in the opposite direction to the rotational force R, and the gravity G act on the oil discharged through the first oil hole H1 .

Here, the rotational force (R) means a force acting in the normal direction of the outer peripheral surface of the rotation shaft (100). The inertial force (I) refers to a force acting in the opposite direction to the direction in which an object is accelerated by receiving an external force (here, a rotational force (R)). Since the inertial force (I) can be described by Newton's first law of motion, a detailed description thereof will be omitted here. Gravity (G) refers to the force that attracts the earth and an object to each other.

Since the inertial force I is a virtual force generated by the rotational force R, only the inertial force I and the gravity G substantially act on the oil discharged through the first oil hole H1. At this time, the force due to the differential pressure C through which the oil is discharged through the first oil hole H1 is relatively smaller than the inertial force I and the gravity G and can be neglected.

At this time, the first direction A1 in which the first oil groove G1 extends downward is the same as the direction A2 (hereinafter, the second direction) of the inertial force I and the gravity G acting on the oil. can be formed. That is, the first angle θ1 in the first direction A1 and the second angle θ2 in the second direction A2 may be formed to be the same.

However, the present invention is not limited thereto, and a difference between the first angle θ1 and the second angle θ2 may be within a predetermined error range.

Also, the first angle θ1 may be proportional to the average operating speed of the rotation shaft 100 . That is, in the case of a compressor having a large average operating speed of the rotating shaft 100 , the first angle θ1 of the first oil groove G1 may be greater than that of a compressor having a low average operating speed of the rotating shaft 100 .

Similarly, the width X1 of the first oil groove G1 may be proportional to the magnitude of the inertia force I with respect to the average operating speed of the rotation shaft 100 . That is, in the case of a compressor having a high average operating speed of the rotating shaft 100 , the width X1 of the first oil groove G1 may be greater than that of a compressor having a low average operating speed of the rotating shaft 100 .

Consequently, as the first oil groove G1 is formed in the same direction as the direction of the force acting on the oil discharged from the first oil hole H1, the first oil groove G1 is formed in the first oil hole H1. ) can move the oil discharged from the lower side quickly. Accordingly, the first oil groove G1 may quickly provide a sufficient amount of oil into the compression unit 290 .

Through this, the first oil groove G1 may provide a sufficient amount of oil into the compression unit 290 , thereby improving the compression efficiency of the compression unit 290 .

Also, the oil guided along the first oil groove G1 may be spread over the entire outer circumferential surface of the main bearing part MB. Accordingly, the first oil groove G1 smoothly supplies oil to the entire main bearing part MB, thereby preventing wear of the main bearing part. In addition, the reliability of the main bearing part can be secured by preventing wear of the main bearing part MB.

In addition, the oil supplied to the main bearing unit MB may form an oil film between the main bearing unit MB and the rotating shaft 100 to maintain an airtight state.

Furthermore, the oil supplied to the main bearing unit MB may absorb and radiate heat generated during friction between the main bearing unit MB and the rotating shaft 100 .

FIG. 8 is a view for explaining another example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 . However, other components of the compressor except for the first oil groove G1 of FIG. 8 are the same as the example described with reference to FIGS. 1 to 7 , and a description thereof will be omitted.

Referring to FIG. 8 , in the first oil groove G1, one end of the first oil groove G1 is connected to the first oil hole H1, and the other end of the first oil groove G1 has a first small diameter part ( 104) may be formed to be connected to the outer peripheral surface.

That is, the first oil groove G1 may be engraved on the outer peripheral surface of the main bearing part MB and the outer peripheral surface of the first small diameter part 104 .

In this case, the first oil groove G1 may be formed to be inclined in a direction opposite to the rotation direction Wr of the rotation shaft 100 toward the lower portion of the main bearing part MB.

The first oil groove G1 may be inclined to have a first angle θ1 from the center C of the rotation shaft 100 . The first angle θ1 of the first oil groove G1 may have an acute angle (ie, a value between 0 degrees and 90 degrees).

A height Z1 of the first oil groove G1 on the main bearing part MB may be formed to be smaller than a height Z2 of the main bearing part MB.

Also, the height d1 of the first oil groove G1 on the first small diameter portion 104 may be formed to be smaller than the height d2 of the first small diameter portion 104 . However, the present invention is not limited thereto, and the height d1 of the first oil groove G1 on the first small-diameter portion 104 may be the same as the height d2 of the first small-diameter portion 104 . connect.

Also, the width X1 of the first oil groove G1 may be smaller than the diameter X2 of the main bearing part MB. Since the diameter of the first small diameter portion 104 is smaller than the diameter of the main bearing portion MB, the width of the first oil groove G1 may not be greatly affected.

However, when the first angle θ1 of the first oil groove G1 increases, the width X1 of the first oil groove G1 may be formed to be larger than the diameter X2 of the main bearing part MB. .

In addition, unlike shown in the drawings, one end of the first oil groove G1 may be formed to extend upwardly through the first oil hole H1 to be connected to the upper surface of the main bearing part MB.

In this case, the height Z1 of the first oil groove G1 on the main bearing part MB may be formed to be the same as the height Z2 of the main bearing part MB.

As the first oil groove G1 extends to the outer circumferential surface of the first small diameter portion 104 , the first oil groove G1 directs the oil discharged from the first oil hole H1 to the first small diameter portion 104 . can be moved quickly. Accordingly, a sufficient amount of oil quickly moves to the first small-diameter portion 104 .

The oil that has moved to the first small-diameter portion 104 may be provided on the upper surface of the orbiting scroll 240 . The oil supplied to the upper surface of the orbiting scroll 240 may be guided to the intermediate pressure chamber ( S2 in FIG. 2 ) through the pocket groove 180 .

Subsequently, the oil guided to the intermediate pressure chamber S2 may be supplied to the thrust surface of the Oldham ring 150 and the fixed scroll 250 installed between the orbiting scroll 240 and the main frame 230 .

That is, the oil introduced into the intermediate pressure chamber S2 may be sufficiently provided to the thrust surface of the fixed scroll 250 and the Oldham ring 150 . Through this, it is possible to reduce wear of the thrust surface of the fixed scroll 250 and the Oldham ring 150 .

That is, the first oil groove G1 sufficiently supplies oil to the main compression part 290, so that the same effect as in the above-described example (ie, reducing wear, maintaining airtightness, heat dissipation, etc.) is obtained in other examples as well. can be obtained

FIG. 9 is a view for explaining another example of an oil groove formed in the rotary shaft of the compressor of FIG. 1 . However, other components of the compressor except for the first oil groove G1 of FIG. 9 are the same as in the example described above with reference to FIGS. 1 to 7 , and a description thereof will be omitted.

Referring to FIG. 9 , the rotation shaft 100 may rotate in a direction opposite to that of the example described with reference to FIGS. 1 to 7 .

In this case, the first oil groove G1 may be formed to be inclined in a direction opposite to the rotation direction Wr of the rotation shaft 100 toward the lower portion of the main bearing part MB.

The first oil groove G1 illustrated in FIG. 9 has an inclination opposite to that of the first oil groove G1 illustrated in FIG. 5 as the rotation direction of the rotation shaft 100 is changed.

In addition, the first oil groove G1 may be inclined to have a first angle θ1 from the center of the rotation shaft 100 , and the first angle θ1 of the first oil groove G1 is an acute angle (that is, , a value between 0 and 90 degrees).

As described above, the downwardly extending direction of the first oil groove G1 may be the same as the direction of the resultant force of the inertial force I and the gravity G due to the rotation of the rotation shaft 100 .

In this case, the first angle θ1 between the first oil groove G1 and the central axis C of the rotation shaft 100 may be proportional to the average operating speed of the rotation shaft 100 .

Similarly, the width X1 of the first oil groove G1 may be proportional to the magnitude of the inertia force I with respect to the average operating speed of the rotation shaft 100 .

As a result, as the first oil groove G1 is formed in the same direction as the direction of the force acting on the oil discharged from the first oil hole H1, the first oil groove G1 becomes the first oil hole H1. ) can move the oil discharged from the lower side quickly. Accordingly, the first oil groove G1 may provide a sufficient amount of oil in the compression part 290 .

In addition, since oil is smoothly supplied to the main bearing part MB, the same effects as those in the above-described example (ie, reduction of wear, airtight maintenance, heat dissipation, etc.) can be obtained in another example.

In the above, the oil groove structure included in the compressor including the lower compression structure has been described. However, the present invention is not limited thereto, and the oil groove structure included in the compressor described in detail above may be used for the upper compression structure.

In addition, the oil groove structure may be applied to a compressor in which the compression unit and the driving motor are disposed in the transverse direction.

For those of ordinary skill in the art to which the present invention pertains, various substitutions, modifications and changes are possible within the scope of the present invention without departing from the technical spirit of the present invention. is not limited by

210: casing 220: drive motor
226: axis of rotation 230: main frame
240: orbiting scroll 250: fixed scroll
290: compression unit

Claims (19)

a casing in which oil is stored in the internal oil storage space;
a driving motor provided in the inner space of the casing;
a compression unit located at one side of the driving motor and discharging the compressed refrigerant into the inner space of the casing; and
It is coupled to the drive motor and includes an oil supply passage provided therein to guide the oil contained in the oil storage space toward the drive motor, and a rotation shaft having an oil hole penetrating from the oil supply passage to an outer circumferential surface,
An oil groove having one end connected to the oil hole and extending from the oil hole to the oil storage space in a direction opposite to the rotation of the rotation shaft is provided on the outer circumferential surface of the rotation shaft,
A width of the oil groove is proportional to a magnitude of an inertia force vector with respect to an average operating speed of the driving motor.
According to claim 1,
The compression unit,
a main frame provided in the inner space of the casing and disposed on one side of the driving motor;
a fixed scroll provided on one side of the main frame;
and an orbiting scroll positioned between the fixed scroll and the main frame, the orbiting scroll moving in engagement with the fixed scroll to form a compression chamber with the fixed scroll,
The oil groove is formed to overlap the main frame.
3. The method of claim 2,
The rotating shaft is
a main bearing part inserted into the main frame and formed to be supported in a radial direction;
an eccentric part inserted into the orbiting scroll and eccentrically coupled;
and a sub bearing part inserted into the fixed scroll and formed to be supported in a radial direction,
The oil groove is formed on an outer circumferential surface of the main bearing part.
4. The method of claim 3,
A height of the oil groove is smaller than a height of the main bearing part.
4. The method of claim 3,
The other end of the oil groove is disposed adjacent to the small diameter portion between the main bearing portion and the eccentric portion,
The oil guided upward through the oil supply passage is discharged through the oil hole, and is guided along the oil groove to be supplied to the outer peripheral surface of the main bearing and the small diameter portion.
4. The method of claim 3,
The rotating shaft further includes a small diameter portion positioned between the main bearing portion and the eccentric portion,
The oil groove extends to an outer peripheral surface of the small-diameter part.
4. The method of claim 3,
The oil groove is formed by engraving on an outer peripheral surface of the main bearing part in an oblique or spiral shape.
According to claim 1,
The oil groove is formed in the same direction as a resultant direction of an inertia force vector generated by a rotational force of the rotary shaft acting on the position of the oil hole and a gravity vector acting on oil discharged from the oil hole.
delete According to claim 1,
The compression unit is located in the casing under the driving motor.
a casing comprising an interior space;
a driving motor provided in the inner space of the casing to generate a rotational force;
a main frame provided in the inner space of the casing and disposed on one side of the driving motor;
a fixed scroll provided on one side of the main frame;
an orbiting scroll positioned between the fixed scroll and the main frame, the orbiting scroll moving in engagement with the fixed scroll to form a compression chamber with the fixed scroll; and
and a rotating shaft that transmits the rotational force generated by the driving motor to the orbiting scroll and has an oil supply flow path formed therein;
An oil groove is provided on the outer circumferential surface of the rotating shaft, overlapping the main frame and extending toward the lower portion of the casing by being inclined in a direction opposite to the rotation of the rotating shaft,
A width of the oil groove is proportional to a magnitude of an inertia force vector with respect to an average operating speed of the driving motor.
12. The method of claim 11,
An intermediate pressure chamber is formed between the main frame, the fixed scroll and the orbiting scroll,
a pocket groove for guiding the oil discharged through the oil groove into the intermediate pressure chamber is formed on an upper surface of the orbiting scroll.
13. The method of claim 12,
The oil guided to the intermediate pressure chamber is supplied to an Oldham ring installed between the orbiting scroll and the main frame and a thrust surface of the fixed scroll.
12. The method of claim 11,
The fixed scroll includes a fixed scroll head plate portion, a fixed scroll side wall portion formed to protrude upwardly from an outer periphery of the fixed scroll end plate portion, and a fixed wrap protruding from an upper surface of the fixed scroll end plate portion;
The orbiting scroll includes a rotating scroll end plate portion provided with a rotating shaft coupling portion so that the rotating shaft is inserted and eccentrically coupled, and an orbiting wrap protruding from the orbiting scroll end plate portion and engaged with the fixed wrap to form the compression chamber. .
12. The method of claim 11,
The rotating shaft is
a main bearing part inserted into the main frame and formed to be supported in a radial direction;
an eccentric part inserted into the orbiting scroll and eccentrically coupled;
and a sub bearing part inserted into the fixed scroll and formed to be supported in a radial direction,
The oil groove is formed on an outer circumferential surface of the main bearing part.
16. The method of claim 15,
The rotating shaft further includes a small diameter portion positioned between the main bearing portion and the eccentric portion,
The oil groove extends to an outer peripheral surface of the small-diameter part.
a casing in which oil is stored in the internal oil storage space;
a driving motor provided in the inner space of the casing;
a compression unit located under the driving motor and discharging the compressed refrigerant into the inner space of the casing; and
It is coupled to the drive motor, and an oil supply passage is provided to guide the oil contained in the oil storage space of the casing toward the drive motor, and includes a rotating shaft having an oil hole penetrating from the oil supply passage to an outer circumferential surface,
An oil groove formed in the same direction as the direction of the resultant force of the inertial force vector acting on the oil discharged from the oil hole and generated by the rotational force of the rotating shaft and the gravity vector acting on the oil is provided on the outer circumferential surface of the rotating shaft,
An angle between the oil groove and the central axis of the rotating shaft is proportional to an average operating speed of the rotating shaft.
delete 18. The method of claim 17,
The width of the oil groove is proportional to the magnitude of the inertia force vector with respect to the average operating speed of the driving motor.

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