Scroll compressor

Abstract

The present invention relates to a scroll compressor comprising: a fixed scroll; an orbiting scroll engaged with the fixed scroll; a driving shaft which drives the orbiting scroll; and a bearing disposed between the orbiting scroll and the driving shaft, wherein the driving shaft comprises a rotating portion rotated by a driving source, and an orbiting portion orbiting with respect to the rotating portion, the bearing is formed as a sliding bearing comprising an outer circumference fitted into the orbiting scroll and an inner circumference that can come into contact with the outer circumference of the orbiting portion. In addition, the inner diameter of the bearing is formed to be greater than the outer diameter of the orbiting portion so that an oil clearance for supplying an oil is formed between the inner circumference of the bearing and the outer circumference of the orbiting portion, thereby reducing the weight and costs and improving durability.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of compressing a refrigerant using a fixed scroll and an orbiting scroll.

[0002] Typically, automobiles are equipped with an air conditioning (A / C) system for cooling and heating the interior. This air conditioning system, as a component of the cooling system, includes a compressor that compresses low-temperature, low-pressure gaseous refrigerant introduced from an evaporator into high-temperature, high-pressure gaseous refrigerant and sends it to a condenser.

[0003] The above compressors include a reciprocating type that compresses the refrigerant through the reciprocating motion of a piston, and a rotary type that compresses through a rotary motion. The reciprocating type includes a crank type that transmits power to multiple pistons using a crank, and a swash plate type that transmits power through a rotating shaft with a swash plate installed, depending on the power transmission method. The rotary type includes a vane rotary type that uses a rotating rotary shaft and vanes, and a scroll type that uses an orbiting scroll and a fixed scroll.

[0004] Among these, scroll compressors are widely used for refrigerant compression in air conditioning systems because they can achieve a relatively high compression ratio compared to other types of compressors, and because the suction, compression, and discharge cycles of the refrigerant are smoothly connected to obtain stable torque.

[0005] Fig. 1 is a cross-sectional view illustrating a conventional scroll compressor, and Fig. 2 is an exploded perspective view illustrating a rotating scroll and parts assembled thereto in the scroll compressor of Fig. 1.

[0006] Referring to FIGS. 1 and 2, a conventional scroll compressor includes a fixed scroll (20), a rotating scroll (30) engaged with the fixed scroll (20), a drive shaft (51) rotated by a drive source (60), an eccentric bush (52) that rotates together with the drive shaft (51) and causes the rotating scroll (30) to rotate, and a bearing (40) interposed between the rotating scroll (30) and the eccentric bush (52).

[0007] Here, the eccentric bush (52) includes a recessed portion (52a) into which the driving shaft (51) is inserted, an eccentric portion (52b) protruding from the recessed portion (52a) to the opposite side of the driving shaft (51) at an eccentric position relative to the driving shaft (51), and a balance weight portion (52c) formed on the opposite side of the eccentric portion (52b) based on the center of the recessed portion (52a), and the bearing (40) is formed as a rolling bearing having an outer ring (42) whose outer circumference is press-fitted into the orbiting scroll (30), an inner ring (44) which is accommodated in the inner circumference of the outer ring (42) and whose inner circumference is press-fitted into the outer circumference of the eccentric portion (52b), and a ball (46) or roller interposed between the outer ring (42) and the inner ring (44).

[0008] However, in such conventional scroll compressors, since the bearing (40) is formed as a cloud bearing, not only does the weight and cost of the bearing (40) increase, but also the centrifugal force of the assembly of the bearing (40) and the orbiting scroll (30) increases during operation, so that the weight and cost of the balance weight part (52c) must increase, and the lifespan of the bearing (40) is reduced. In other words, there was a problem in that the weight and cost increased and the durability was reduced.

[0009] Accordingly, the present invention aims to provide a scroll compressor capable of reducing weight and cost and improving durability.

[0010] The present invention provides a scroll compressor for achieving the above-described object, comprising: a fixed scroll; an orbiting scroll meshed with the fixed scroll; a drive shaft for driving the orbiting scroll; and a bearing interposed between the orbiting scroll and the drive shaft, wherein the drive shaft includes a rotating part rotated by a driving source and a rotating part that rotates around the rotating part, and the bearing is formed as a sliding bearing having an outer circumferential surface press-fitted to the orbiting scroll and an inner circumferential surface contactable with the outer circumferential surface of the orbiting part, and an inner diameter of the bearing is formed larger than an outer diameter of the orbiting part so that an oil clearance for supplying oil is formed between the inner circumferential surface of the bearing and the outer circumferential surface of the orbiting part.

[0011] A back pressure chamber is provided for pressurizing the above-mentioned rotating scroll toward the above-mentioned fixed scroll side, and the oil clearance can be communicated with the back pressure chamber.

[0012] The above-mentioned turning scroll includes an annular boss portion into which the bearing is pressed, and a front end surface of the turning portion is formed to be spaced apart from a base surface of the boss portion, so that a gap is formed between the front end surface of the turning portion and the base surface of the boss portion, and the oil clearance can be communicated with the gap.

[0013] The above-mentioned turning part may include an internal oil channel penetrating the above-mentioned turning part, and the internal oil channel may include a first opening communicating with the back pressure chamber, a second opening communicating with the gap, and a communication path connecting the first opening and the second opening.

[0014] The first opening and the second opening may each be formed in a circular groove shape having a predetermined depth.

[0015] The inner diameter of the above first opening may be formed to be larger than the inner diameter of the above-mentioned passage.

[0016] The inner diameter of the above second opening may be formed to be larger than the inner diameter of the above-mentioned passage.

[0017] The inner diameter of the first opening may be formed to be larger than the inner diameter of the passage, and the inner diameter of the second opening may be formed to be larger than the inner diameter of the first opening.

[0018] The depth of the second opening may be formed deeper than the depth of the first opening.

[0019] The above-mentioned pivot member may be formed in a cylindrical shape having a front end surface facing the gap, a back surface of the front end surface, a bottom surface that can contact the front end surface of the rotating member, and an outer surface that can contact the inner surface of the bearing.

[0020] The above-mentioned pivot member may include a slit formed concavely from the bottom surface and opening to the outer surface.

[0021] The first opening may be formed engraved in the slit, and the second opening may be formed engraved in the leading edge surface of the pivot member.

[0022] The above-mentioned chimney can be formed so that it moves away from the central axis of the pivot as it moves toward the second opening.

[0023] The above-mentioned turning part may include an external oil channel formed concavely on an outer surface of the turning part, and the external oil channel may include a first opening communicating with the back pressure chamber, a second opening communicating with the gap, and a communication path connecting the first opening and the second opening.

[0024] The above-mentioned communication path may include at least one first communication path extending axially in a circumferential direction and a second communication path extending circumferentially and intersecting the at least one first communication path.

[0025] A scroll compressor according to the present invention comprises: a fixed scroll; an orbiting scroll meshed with the fixed scroll; a drive shaft for driving the orbiting scroll; and a bearing interposed between the orbiting scroll and the drive shaft, wherein the drive shaft includes a rotating part rotated by a driving source and a rotating part that rotates around the rotating part, and the bearing is formed as a sliding bearing having an outer circumferential surface press-fitted to the orbiting scroll and an inner circumferential surface contactable with the outer circumferential surface of the orbiting part, and an inner diameter of the bearing is formed larger than an outer diameter of the orbiting part so that an oil clearance for supplying oil is formed between the inner circumferential surface of the bearing and the outer circumferential surface of the orbiting part, thereby reducing weight and cost and improving durability.

[0026] Figure 1 is a cross-sectional view showing a conventional scroll compressor;

[0027] Figure 2 is an exploded perspective view showing the rotating scroll and the parts assembled thereto in the scroll compressor of Figure 1.

[0028] Figure 3 is a cross-sectional view illustrating a scroll compressor according to one embodiment of the present invention;

[0029] Figure 4 is an enlarged view of part A of Figure 3.

[0030] Figure 5 is an exploded perspective view showing the components of Figure 4;

[0031] Fig. 6 is a perspective view showing a driving shaft among the components of Fig. 4.

[0032] Figure 7 is a front view of Figure 6;

[0033] Figure 8 is an enlarged view of part B of Figure 7.

[0034] Figure 9 is a front view showing a drive shaft in a scroll compressor according to another embodiment of the present invention;

[0035] Figure 10 is an enlarged view of part C of Figure 9.

[0036] FIG. 11 is a perspective view showing a rotating part of a drive shaft in a scroll compressor according to another embodiment of the present invention;

[0037] Fig. 12 is a cross-sectional view of Fig. 11.

[0038] Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to the attached drawings.

[0039] FIG. 3 is a cross-sectional view illustrating a scroll compressor according to one embodiment of the present invention, FIG. 4 is an enlarged view of part A of FIG. 3, a cross-sectional view cut from a different position to show an internal channel, FIG. 5 is an exploded perspective view illustrating parts of FIG. 4, FIG. 6 is a perspective view illustrating a drive shaft among the parts of FIG. 4, FIG. 7 is a front view of FIG. 6, and FIG. 8 is an enlarged view of part B of FIG. 7.

[0040] Referring to FIGS. 3 to 8, a scroll compressor according to one embodiment of the present invention may include a casing (100), a fixed scroll (200) fixed to the casing (100), an orbiting scroll (300) that is engaged with the fixed scroll (200) and forms a compression chamber, a driving shaft (500) that drives the orbiting scroll (300), and a bearing (400) interposed between the orbiting scroll (300) and the driving shaft (500).

[0041] The casing (100) includes a main frame (112) that supports the orbiting scroll (300), and the main frame (112) may include a shaft hole (112a) into which a rotational part (510) of the driving shaft (500) to be described later is inserted, and a back pressure chamber (112b) that is formed to be in communication with the shaft hole (112a) and provides a space in which the rotational part (520) of the driving shaft (500) to be described later can rotate, and receives oil for pressurizing the orbiting scroll (300) toward the fixed scroll (200).

[0042] The above fixed scroll (200) may include a fixed plate (210) in the shape of a disk and a fixed wrap (220) protruding from the fixed plate (210) toward the rotating scroll (300).

[0043] The above-described rotary scroll (300) may include a circular rotary plate (310), a rotary wrap (320) that protrudes from the rotary plate (310) toward the fixed scroll (200) and engages with the fixed wrap (220), and an annular boss portion (330) that protrudes from the rotary plate (310) toward the opposite side of the rotary wrap (320).

[0044] Here, if the surface facing the inner circumference of the boss portion (330) in the above-described turning plate (310) is referred to as the base surface (314) of the boss portion (330), the base surface (314) of the boss portion (330) is spaced apart from the front end surface of the turning portion (520) to be described later, so that a gap (G) is formed between the base surface (314) of the boss portion (330) and the front end surface of the turning portion (520) to be described later, and the gap (G) contributes to supplying oil between the bearing (400) and the turning portion (520) to be described later, which will be described later.

[0045] The above driving shaft (500) may include a rotating part (510) that is rotated by a driving source (600), such as a motor, for example, and a rotating part (520) that is eccentrically coupled to the rotating part (510) and inserted into the boss part (330) to rotate about the rotating part (510) and to rotate the rotating scroll (300).

[0046] The bearing (400) may be formed as a sliding bearing having an outer circumferential surface (410) press-fitted into the inner circumferential surface of the boss portion (330) and an inner circumferential surface (420) contactable with the outer circumferential surface (522) of the pivot portion (520). Accordingly, weight and cost can be reduced and durability can be improved. Specifically, not only is the radial thickness of the bearing (400) smaller than the axial length, but the number of parts is also reduced, so that the weight and cost of the bearing (400) can be reduced. In addition, the centrifugal force of the assembly of the bearing (400) and the pivot scroll (300) during operation is reduced, so that the lifespan of the bearing (400) can be increased. In addition, the weight and cost of the balance weight, which will be described later, can also be reduced.

[0047] Here, the sliding bearing can be classified into a split sliding bearing composed of at least two parts and an integral bush-type sliding bearing. In terms of cost reduction, wear prevention, etc., it may be preferable for the bearing (400) to be formed as a bush-type sliding bearing.

[0048] And, since the bearing (400) is formed as a sliding bearing, it is important to manage the surface roughness between the inner surface (420) of the bearing (400) and the outer surface (522) of the turning part (520). In order to manage the surface roughness of the outer surface of the turning part (520) to be lower than the surface roughness of other parts of the turning part (520) at a low cost while also improving productivity, it may be preferable that the rotating part (510) and the turning part (520) are formed as separate bodies and then assembled, as in the present embodiment.

[0049] And, since the bearing (400) is formed as a sliding bearing, it is important to suppress uneven wear between the inner surface (420) of the bearing (400) and the outer surface (522) of the pivot member (520). In order to suppress tilting of the pivot member (520) and suppress uneven wear between the inner surface (420) of the bearing (400) and the outer surface (522) of the pivot member (520), as in the present embodiment, it may be preferable that the pivot member (520) be formed in a cylindrical shape in which a circular bottom surface (524) can contact the front end surface (516) of the rotating part (510), the front end surface (526), ​​which is the back surface of the bottom surface (524), faces the base surface (314) of the boss portion (330), and the outer surface (522) can contact the inner surface (420) of the bearing (400). That is, unlike the conventional eccentric bush (52), it may be desirable for the pivot member (520) to be formed as a separate body from a balance weight placed on the opposite side of the pivot member (520) with respect to the rotation axis of the pivot member (510) in order to maintain rotational balance.

[0050] And, since the bearing (400) is formed as a sliding bearing, lubrication between the inner surface (420) of the bearing (400) and the outer surface (522) of the pivot member (520) is important. Taking this into consideration, it may be preferable that the inner diameter of the bearing (400) be formed larger than the outer diameter of the pivot member (520) so that an oil clearance (CR) for supplying oil is formed between the inner surface (420) of the bearing (400) and the outer surface (522) of the pivot member (520).

[0051] In addition, since the oil's viscosity decreases and the oil film is destroyed as the temperature rises, resulting in a deterioration in lubricating performance, it may be desirable to replace the oil lubricating the friction part with a different oil. Taking this into account, in the present embodiment, the oil in the oil clearance (CR) may be configured to be replaced with a different oil.

[0052] Specifically, in this embodiment, the oil clearance (CR) is formed to be in communication with the back pressure chamber (112b) and the gap (G), the pivot member (520) includes an internal oil channel (I) penetrating the pivot member (520), and the internal oil channel (I) includes an internal oil channel first opening (I1) communicating with the back pressure chamber (112b), an internal oil channel second opening (I2) communicating with the gap (G), and an internal oil channel communication path (I3) connecting the internal oil channel first opening (I1) and the internal oil channel second opening (I2), so that oil sequentially passes through the back pressure chamber (112b), the internal oil channel (I), and the gap (G) to be supplied to the oil clearance (CR), and the oil of the oil clearance (CR) is supplied to the inner surface (420) of the bearing (400) and the It can be formed to repeat the process of lubricating the outer surface (522) of the pivot (520) and then returning to the back pressure chamber (112b).

[0053] Here, in order to promote the circulation of oil, the internal oil channel first opening (I1), the internal oil channel second opening (I2), and the internal oil channel communication path (I3) can each be formed in a predetermined shape.

[0054] That is, in order to operate as an oil capture for increasing the amount of oil flowing from the back pressure chamber (112b) to the internal oil channel (I) by using surface tension, the internal oil channel first opening (I1) is formed in a circular groove shape having a predetermined depth, and the inner diameter of the internal oil channel first opening (I1) can be formed to be larger than the inner diameter of the internal oil channel communication passage (I3).

[0055] For reference, an engraved slit (524b) is formed on the bottom surface (524) of the pivot member (520), the slit (524b) extends in the radial direction of the pivot member and opens to the outer circumferential surface (522) of the pivot member (520), and the first internal oil channel opening (I1) is engravedly formed in the slit (524b), so that oil in the back pressure chamber (112b) can be supplied to the first internal oil channel opening (I1) through the slit (524b) and also between the front end surface (516) of the rotating member (510) and the bottom surface (524) of the pivot member (520).

[0056] And, so that the internal oil channel second opening (I2) operates as an oil chamber for storing a certain amount of oil to stably supply oil to the oil clearance (CR), the internal oil channel second opening (I2) is formed in a circular groove shape with a certain depth, and the inner diameter of the internal oil channel second opening (I2) can be formed to be larger than the inner diameter of the internal oil channel communication passage (I3).

[0057] In addition, the inner diameter of the inner oil channel second opening (I2) may be formed to be larger than the inner diameter of the inner oil channel first opening (I1) so that the amount of oil that the inner oil channel second opening (I2) stores is greater than the amount of oil that the inner oil channel first opening (I1) captures. In addition, the depth (D2) of the inner oil channel second opening (I2) may be formed to be deeper than the depth (D1) of the inner oil channel first opening (I1).

[0058] And, so that the oil in the internal oil channel communication path (I3) can smoothly flow from the internal oil channel first opening (I1) to the internal oil channel second opening (I2) by centrifugal force, the internal oil channel communication path (I3) can be formed to move away from the central axis of the pivot (520) toward the second opening.

[0059] Here, the circulation direction of the oil may vary depending on the extension direction of the internal oil channel communication path (I3).

[0060] Specifically, when the internal oil channel communication path (I3) is formed to get closer to the central axis of the pivot member (520) as it goes toward the second opening, the oil may be circulated in the opposite manner to that described above. That is, the oil of the internal oil channel communication path (I3) flows from the internal oil channel second opening (I2) to the internal oil channel first opening (I1) by centrifugal force, and accordingly, the oil of the back pressure chamber (112b) is supplied to the oil clearance (CR), and the oil of the oil clearance (CR) lubricates the space between the inner surface (420) of the bearing (400) and the outer surface (522) of the pivot member (520), and then sequentially passes through the gap (G) and the internal oil channel (I) to return to the back pressure chamber (112b), a process that can be repeated.

[0061] Alternatively, the internal oil channel communication path (I3) may be formed so that the distance from the central axis of the pivot member (520) is constant regardless of the extension direction of the internal oil channel communication path (I3), and in this case, the oil may sequentially pass through the back pressure chamber (112b), the internal oil channel (I), the gap (G), and the oil clearance (CR) depending on the situation and then return to the back pressure chamber (112b), or may pass through the back pressure chamber (112b), the oil clearance (CR), the gap (G), and the internal oil channel (I) and then return to the back pressure chamber (112b).

[0062] In any case, the oil in the oil clearance (CR) can be replaced with other oil, but in order to prevent a temporary oil circulation stoppage due to a change in the circulation direction, it is preferable that the internal oil channel communication path (I3) be formed to be closer to or farther away from the central axis of the pivot (520) as it goes toward the second opening, and in order to allow the internal oil channel first opening (I1) to operate as an oil capture while the internal oil channel second opening (I2) to operate as an oil chamber, it may be more preferable that the internal oil channel communication path (I3) be formed to be farther away from the central axis of the pivot (520) as it goes toward the second opening.

[0063] Meanwhile, in order to prevent damage to the rotating scroll (300) and the fixed scroll (200) due to compression of the liquid refrigerant, such as during initial operation, the rotating radius of the rotating scroll (300) needs to be formed to be variable, and in consideration of this, the rotating part (520) can be formed to be capable of swinging relative to the rotating part (510) based on the drive pin (530) connecting the rotating part (520) and the rotating part (510).

[0064] Specifically, the drive pin (530) is formed in a cylindrical shape extending in a direction parallel to the axial direction of the rotating part (510), a drive pin groove (517) into which one end of the drive pin (530) is inserted is formed in the rotating part (510), and a drive pin hole (527) into which the other end of the drive pin (530) is inserted may be formed in the pivot part (520).

[0065] The drive pin groove (517) may be formed at a position where the center of the drive pin groove (517) is spaced apart from the rotation axis of the rotation unit (510) in the radial direction of the rotation unit (510) so that the center axis of the drive pin (530) is positioned eccentrically with respect to the rotation axis of the rotation unit (510).

[0066] The drive pin hole (527) may be formed at a position where the center of the drive pin hole (527) is spaced apart from the center axis of the pivot unit (520) in the radial direction of the pivot unit (520) so that the center axis of the drive pin (530) is positioned eccentrically with respect to the center axis of the pivot unit (520).

[0067] Here, in the present embodiment, the drive pin groove (517) is formed in the rotating part (510) and one end of the drive pin (530) is inserted into the drive pin groove (517), but this is not limited thereto. That is, the rotating part (510) and the drive pin (530) may be formed integrally.

[0068] And, in order to prevent the pivot part (520) from being axially separated from the rotating part (510), the drive pin hole (527) is formed to penetrate the pivot part (520) in the axial direction from the bottom surface (524) of the pivot part (520) to the front end surface (526) of the pivot part (520), and the other end of the drive pin (530) is formed to protrude to the opposite side of the rotating part (510) based on the pivot part (520) by penetrating the drive pin hole (527), and when the portion of the other end of the drive pin (530) that is exposed to the outside of the drive pin hole (527) is referred to as an exposed end (534a), a retainer (540) that is fixed to the exposed end (534a) and prevents the pivot part (520) from being axially separated from the rotating part (510) may be provided.

[0069] In addition, it is necessary to limit the swing motion range of the pivot part (520) so that it does not collide with other parts when the pivot part (520) swings. In terms of suppressing cost increase, it may be desirable for the retainer (540) to be formed to limit the swing motion range of the pivot part (520) while preventing the pivot part (520) from being detached. To this end, as in the present embodiment, the retainer (540) includes a retainer extension (542) extending radially outward, and the retainer extension (542) includes a first retainer extension (542a) and a second retainer extension (542b) spaced apart from each other in the circumferential direction, and the pivot (520) is formed at an eccentric position with respect to the drive pin (530) and protrudes from the inner surface of the second internal oil channel opening (I2) and includes a swing limiting protrusion (P) positioned between the first retainer extension (542a) and the second retainer extension (542b), and the distance in the swing motion direction between the first retainer extension (542a) and the second retainer extension (542b) is formed to be larger than the swing motion direction width of the swing limiting protrusion (P), and the retainer (540) is formed in advance so that deformation does not occur relatively easily. It is formed to have an elastic modulus (= stress / strain) greater than or equal to a determined value, so that the range of movement of the swing limiting protrusion (P) can be regulated by the distance in the swing movement direction between the first retainer extension (542a) and the second retainer extension (542b).

[0070] However, it is not limited thereto. That is, as illustrated in FIGS. 9 and 10, the retainer (540) includes the retainer extension (542), and the pivot (520) is formed concavely on the inner surface of the second internal oil channel opening (I2) and includes the swing limiting groove (S) that receives the end of the retainer extension (542), and the swing motion direction width of the swing limiting groove is formed to be larger than the swing motion direction width of the end of the retainer extension (542), so that the movement range of the swing limiting groove (S) can be regulated by the swing motion direction distance between the swing suggestion groove (S) and the retainer extension (542). Alternatively, although not shown separately, the retainer (540) may be formed to have an elastic coefficient smaller than a predetermined value so that the range of movement of the pivot (520) is regulated by the range of elastic deformation of the retainer extension (542), and the swing motion direction width of the swing limiting protrusion (P) may be formed to be equal to the swing motion direction distance between the first retainer extension (542a) and the second retainer extension (542b), or the swing motion direction width of the swing limiting groove (S) may be formed to be equal to the swing motion direction width of the end of the retainer extension (542).

[0071] Meanwhile, in the present embodiment, the pivot part (520) includes the internal oil channel (I), but is not limited thereto.

[0072] That is, as illustrated in FIGS. 11 and 12, the pivot member (520) includes an external oil channel (O) engraved on the outer surface (522) of the pivot member (520) instead of the internal oil channel (I), and the external oil channel (O) may include an external oil channel first opening (O1) communicating with the back pressure chamber (112b), an external oil channel second opening (O2) communicating with the gap (G), and an external oil channel communication path (O3) connecting the external oil channel first opening (O1) and the external oil channel second opening (O2). In this case, the amount of oil supplied between the bearing (400) and the pivot member (520) increases, but oil circulation may not be smooth.

[0073] Here, in order to more evenly supply a larger amount of oil between the bearing (400) and the pivot member (520), the external oil channel communication path (O3) may include at least one first external oil channel communication path (O31) extending in the axial direction and a second external oil channel communication path (O32) extending in the circumferential direction and intersecting the at least one first external oil channel communication path (O31).

[0074] Alternatively, although not shown separately, the pivot member (520) may include both the internal oil channel (I) and the external oil channel (O). In this case, the oil circulation may be smooth, and the amount of oil supplied between the bearing (400) and the pivot member (520) may increase.

[0075] Meanwhile, the structure in which oil is circulated and supplied to the inner surface (420) of the bearing (400) does not presuppose that the pivot part (520) is provided. That is, although not separately illustrated, when the bearing (400) is formed as a sliding bearing, although it is disadvantageous in terms of uneven wear, the pivot part (520) can be applied as a conventional eccentric bush (52), and at this time, an oil clearance (CR) is provided between the outer circumferential surface of the eccentric part (52b) of the eccentric bush (52) and the inner circumferential surface (420) of the bearing (400), and the oil clearance (CR) is connected to the back pressure chamber (112b) and the gap (G) between the front end surface of the eccentric part (52b) and the base surface (314) of the boss part (330), and at least one of an internal oil channel (I) penetrating the eccentric bush (52) and an external oil channel (O) engravedly formed on the outer circumferential surface of the eccentric bush (52) can be formed.

Claims

1. Fixed scroll; A pivoting scroll that engages with the above fixed scroll; a drive shaft for driving the above-mentioned rotary scroll; and A bearing interposed between the above-mentioned rotary scroll and the above-mentioned driving shaft; The above drive shaft includes a rotating part that is rotated by a driving source and a rotating part that rotates based on the rotating part, The above bearing is formed as a sliding bearing having an outer surface that is pressed into the above-mentioned rotating scroll and an inner surface that can contact the outer surface of the rotating part, A scroll compressor in which the inner diameter of the bearing is formed larger than the outer diameter of the pivot portion so that an oil clearance for oil supply is formed between the inner circumference of the bearing and the outer circumference of the pivot portion.

2. In paragraph 1, Further comprising a back pressure chamber for pressurizing the above-mentioned rotating scroll toward the above-mentioned fixed scroll side, The above oil clearance is a scroll compressor communicating with the above back pressure chamber.

3. In paragraph 2, The above-mentioned rotary scroll includes an annular boss portion into which the bearing is pressed, The leading edge of the above-mentioned turning part is formed to be spaced apart from the base surface of the above-mentioned boss part, so that a gap is formed between the leading edge of the above-mentioned turning part and the base surface of the above-mentioned boss part. The above oil clearance is a scroll compressor in communication with the above gap.

4. In paragraph 3, The above turning part includes an internal oil channel penetrating the turning part, A scroll compressor, wherein the internal oil channel includes a first opening communicating with the back pressure chamber, a second opening communicating with the gap, and a communication path connecting the first opening and the second opening.

5. In paragraph 4, A scroll compressor in which the first opening and the second opening are each formed in a circular groove shape having a predetermined depth.

6. In paragraph 5, A scroll compressor in which the inner diameter of the first opening is formed larger than the inner diameter of the combustion passage.

7. In paragraph 5, A scroll compressor in which the inner diameter of the second opening is formed larger than the inner diameter of the combustion passage.

8. In paragraph 7, The inner diameter of the above first opening is formed to be larger than the inner diameter of the above-mentioned passage, A scroll compressor in which the inner diameter of the second opening is formed larger than the inner diameter of the first opening.

9. In paragraph 5, A scroll compressor in which the depth of the second opening is formed deeper than the depth of the first opening.

10. In paragraph 4, A scroll compressor in which the above-mentioned rotating part is formed in a cylindrical shape having a front end surface facing the gap, a back surface of the front end surface, a bottom surface that can contact the front end surface of the rotating part, and an outer surface that can contact the inner surface of the bearing.

11. In paragraph 10, A scroll compressor in which the above-mentioned turning part is formed concavely from the bottom surface and includes a slit that opens to the outer surface.

12. In paragraph 11, A scroll compressor in which the first opening is formed engraved in the slit, and the second opening is formed engraved in the leading edge surface of the turning section.

13. In paragraph 4, A scroll compressor in which the above-mentioned chimney is formed to move away from the central axis of the turning part as it moves toward the second opening.

14. In paragraph 3, The above-mentioned turning part includes an external oil channel engraved on the outer surface of the turning part, A scroll compressor, wherein the external oil channel includes a first opening communicating with the back pressure chamber, a second opening communicating with the gap, and a communication path connecting the first opening and the second opening.

15. In paragraph 14, A scroll compressor, wherein the above-mentioned communication path includes at least one first communication path extending axially in a circumferential direction and a second communication path extending circumferentially and intersecting the at least one first communication path.

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