Scroll compressor

Abstract

To provide a scroll compressor which can suppress the lowering in cooling performance of an outside portion of a revolving scroll in a radial direction.SOLUTION: A scroll compressor comprises a cooling fan 25 and a cooling wind introduction path 28 for introducing cooling wind generated by the cooling fan 25 to a periphery of a cooling fin 20 of a revolving scroll 12. The cooling fin 20 includes: an n-th cooling fin located at one side and the outside of the cooling wind introduction path 28 in a width direction of the cooling wind introduction path 28 which is parallel with an arrangement direction of the cooling fin 20; an (n-1)-th cooling fin which adjoins the n-th cooling fin at one side; and an (n+1)-th cooling fin which adjoins the n-th cooling fin at the opposite side. A front edge of the n-th cooling fin is located at a downstream side with respect to a virtual linear line for connecting a front edge of the (n-1)-th cooling fin and a front edge of the (n+1)-th cooling fin.SELECTED DRAWING: Figure 3

Description

Technical Field

[0001] The present invention relates to a scroll compressor for compressing gas.

Background Art

[0002] The scroll compressor of Patent Document 1 includes a fixed scroll, a orbiting scroll facing the fixed scroll, and a drive shaft for orbiting the orbiting scroll with respect to the fixed scroll.

[0003] The fixed scroll has a substantially circular base plate (end plate), a spiral wrap erected on one side surface of the base plate (in other words, the side facing the orbiting scroll), a plurality of cooling fins (radiating fins) erected on the opposite side surface of the base plate, and a lid portion provided on the tip side of the plurality of cooling fins.

[0004] The orbiting scroll has a substantially circular base plate (end plate), a spiral wrap erected on one side surface of the base plate (in other words, the side facing the fixed scroll), a plurality of cooling fins (radiating fins) erected on the opposite side surface of the base plate, and a plate provided on the tip side of the plurality of cooling fins.

[0005] A crank portion is provided on one end side of the drive shaft. This crank portion is eccentric from the center of the drive shaft and is connected to the boss portion of the plate of the orbiting scroll via an orbiting scroll bearing. Therefore, when the drive shaft rotates, the orbiting scroll orbits with respect to the fixed scroll. A plurality of working chambers are formed between the wrap of the fixed scroll and the wrap of the orbiting scroll. Each working chamber moves from the outside to the inside in the direction of wrap extension (in other words, approaches the radial center portion of the orbiting scroll) as the orbiting scroll orbits, and sequentially performs an intake process, a compression process, and a discharge process.

[0006] A cooling fan (blower fan) is provided at the other end of the drive shaft. Therefore, when the drive shaft rotates, the cooling fan rotates and generates cooling air. The cooling air generated by the cooling fan is supplied via a duct to the area around the cooling fins of the fixed scroll (specifically, to the multiple cooling channels formed between the multiple cooling fins) and to the area around the cooling fins of the orbiting scroll (specifically, to the multiple cooling channels formed between the multiple cooling fins). This cools both the fixed scroll and the orbiting scroll. [Prior art documents] [Patent Documents]

[0007] [Patent Document 1] Japanese Patent Publication No. 2018-173051 [Overview of the project] [Problems that the invention aims to solve]

[0008] Although not explicitly stated in Patent Document 1, the cooling air introduction passage that introduces cooling air around the cooling fins of the orbiting scroll is formed such that its width dimension (more specifically, the width dimension parallel to the arrangement direction of the multiple cooling fins) is greater than the overall width dimension of the multiple cooling fins. In this case, the flow rate distribution of the cooling air in the arrangement direction of the multiple cooling fins, in other words, in the radial direction of the orbiting scroll, becomes almost uniform.

[0009] The radially inner portion of the orbiting scroll tends to become hotter than the radially outer portion due to the effects of compression heat. Therefore, it is preferable that the cooling air intake passage described above be formed such that its width is smaller than the total width of the multiple cooling fins. In this case, it is possible to increase the flow rate of cooling air in the radially inner portion of the orbiting scroll compared to the radially outer portion, thereby improving the cooling performance of the radially inner portion of the orbiting scroll.

[0010] Here, the gaps between the multiple cooling fins and the inner wall of the casing need to be of a certain size to avoid interference between them, and tend to be larger than the cooling channels formed between the cooling fins. Therefore, cooling air tends to flow more easily into the aforementioned gaps than into the cooling channels located outside the cooling air inlet passage in the width direction of the cooling air inlet passage. Consequently, the flow rate of cooling air in the radially outer portion of the orbiting scroll may decrease significantly, potentially leading to a significant decrease in the cooling performance of the radially outer portion of the orbiting scroll. If the cooling performance of the radially outer portion of the orbiting scroll decreases significantly, the suction flow rate of the compressor will decrease.

[0011] The present invention has been made in view of the above matters, and one of its objectives is to suppress the decrease in cooling performance of the radially outer portion of the orbiting scroll. [Means for solving the problem]

[0012] In order to solve the above problems, the configuration described in the claims is applied. The present invention includes a plurality of means for solving the above problems, but to give one example, a scroll compressor comprising a fixed scroll having a spiral wrap, a base plate, a spiral wrap erected on one side of the base plate, and a plurality of cooling fins erected on the opposite side of the base plate, a drive shaft for rotating the orbital scroll relative to the fixed scroll, a cooling fan for generating cooling air, and a cooling air introduction passage for introducing the cooling air generated by the cooling fan around the plurality of cooling fins, wherein a plurality of working chambers are formed between the wrap of the fixed scroll and the wrap of the orbital scroll, wherein the plurality of cooling fins are an nth cooling fin located on one side and outside the cooling air introduction passage in the width direction of the cooling air introduction passage parallel to the arrangement direction of the cooling fins, an (n-1)th cooling fin adjacent to the nth cooling fin on the one side, and an (n+1)th cooling fin adjacent to the nth cooling fin on the opposite side , with respect to the (n-1)th cooling fin, the (n-2) cooling fin adjacent to the one side thereof The front edge of the nth cooling fin is located downstream of the imaginary line connecting the front edge of the (n-1)th cooling fin and the front edge of the (n+1)th cooling fin. Furthermore, the leading edge of the (n-1)th cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-2)th cooling fin and the leading edge of the (n+1)th cooling fin. [Effects of the Invention]

[0013] According to the present invention, it is possible to suppress the decrease in cooling performance of the radially outer portion of the orbiting scroll.

[0014] Furthermore, other issues, structures, and effects not mentioned above will be clarified in the following explanation. [Brief explanation of the drawing]

[0015] [Figure 1] This is an axial cross-sectional view showing the structure of a scroll compressor in one embodiment to which the present invention is applied. [Figure 2] This is a radial cross-sectional view taken along the line II-II in Figure 1, illustrating the structure of the cooling fins of the orbiting scroll. [Figure 3] This is a partially enlarged view of part III of Figure 2, showing the position of the leading edge of the cooling fins located on one side in the width direction of the cooling air intake passage. [Figure 4] This is a partially enlarged view showing the position of the leading edge of the cooling fins arranged on one side in the width direction of the cooling air intake in the comparative example. [Figure 5] This is a radial cross-sectional view showing the structure of the cooling fins of a revolving scroll in one modified example to which the present invention is applied. [Figure 6] This is a partially enlarged view of part VI of Figure 5, showing the position of the leading edge of the cooling fins located on one side in the width direction of the cooling air intake passage. [Modes for carrying out the invention]

[0016] An embodiment of the present invention will be described with reference to the drawings.

[0017] FIG. 1 is an axial cross-sectional view showing the structure of the scroll compressor according to the present embodiment. FIG. 2 is a radial cross-sectional view taken along the arrow II-II in FIG. 1, showing the structure of the cooling fins of the orbiting scroll. FIG. 3 is a partial enlarged view taken along the portion III in FIG. 2, showing the position of the leading edge of the cooling fins arranged on one side in the width direction of the cooling air introduction passage. Note that the white arrows in FIG. 1 and the dotted arrows in FIGS. 2 and 3 indicate the flow of the cooling air.

[0018] The scroll compressor according to the present embodiment includes a casing 10, a fixed scroll 11, an orbiting scroll 12, and a drive shaft 13. The fixed scroll 11 is connected to the opening side (the upper side in FIG. 1) of the casing 10. The orbiting scroll 12 is housed in the casing 10 and faces the fixed scroll 11. The drive shaft 13 is rotatably supported by a bearing 14 in the casing 10.

[0019] The fixed scroll 11 has a substantially circular base plate, a spiral wrap 15 erected on one side surface (the lower side in FIG. 1) of the base plate, a plurality of cooling fins erected on the opposite side surface (the upper side in FIG. 1) of the base plate, and a lid portion provided on the tip side (the upper side in FIG. 1) of the plurality of cooling fins. An intake passage (not shown) is formed in the radially outer portion of the base plate of the fixed scroll 11, and an intake filter 16 is connected to this intake passage. A discharge passage is formed in the radially central portion of the base plate of the fixed scroll 11, and a discharge pipe 17 is connected to this discharge passage.

[0020] The orbiting scroll 12 has a substantially circular base plate 18, a spiral wrap 19 erected on one side surface (the upper side in FIG. 1) of the base plate 18, a plurality of cooling fins 20 erected on the opposite side surface (the lower side in FIG. 1) of the base plate 18, and a plate 21 provided on the tip side (the lower side in FIG. 1) of the plurality of cooling fins 20.

[0021] A crank portion 22 is provided on one end side (the upper side in FIG. 1) of the drive shaft 13. The crank portion 22 is eccentric from the center of the drive shaft 13 and is connected to the boss portion of the plate 21 of the orbiting scroll 12 via a swivel bearing 23.

[0022] The other end of the drive shaft 13 (the lower side in Figure 1) protrudes outside the casing 10 and is equipped with a pulley 24. A belt (not shown) is stretched between a pulley (not shown) on the rotating shaft of the electric motor (not shown) and the pulley 24. This transmits the rotational force of the electric motor, causing the drive shaft 13 to rotate and the orbiting scroll 12 to orbit relative to the fixed scroll 11. A rotation prevention mechanism is provided inside the casing 10 to prevent the orbiting scroll 12 from rotating on its own.

[0023] Multiple working chambers are formed between the wrap 15 of the fixed scroll 11 and the wrap 19 of the orbiting scroll 12. Each working chamber moves from the outside to the inside in the direction of wrap extension (in other words, towards the radial center of the orbiting scroll 12) as the orbiting scroll 12 rotates, and sequentially performs an intake process, a compression process, and a discharge process. The working chamber in the intake process draws in air (gas) through the intake filter 16 and the intake passage. The working chamber in the compression process compresses the air. The working chamber in the discharge process discharges compressed air (compressed gas) through the discharge passage and the discharge pipe 17.

[0024] The scroll compressor of this embodiment further includes a cooling fan 25 and a duct 26. The cooling fan 25 is, for example, a centrifugal fan provided on the other end of the drive shaft 13, and rotates together with the drive shaft 13 to generate cooling air. The duct 26 supplies the cooling air generated by the cooling fan 25 around the cooling fins of the fixed scroll 11 (specifically, multiple cooling channels formed between the multiple cooling fins) and around the cooling fins 20 of the orbiting scroll 12 (specifically, multiple cooling channels formed between the multiple cooling fins 20). This cools the fixed scroll 11 and the orbiting scroll 12.

[0025] The casing 10 includes a cooling fin housing section 27 for housing the cooling fins 20 of the orbiting scroll 12, a cooling air introduction passage 28 formed upstream of the cooling fin housing section 27 (left side in Figure 2) for introducing cooling air from the guide 26a of the duct 26 around the cooling fins 20 of the orbiting scroll 12, and a cooling air discharge passage 29 formed downstream of the cooling fin housing section 27 (right side in Figure 2) for discharging cooling air from around the cooling fins 20 to the outside. The cooling fin housing section 27, the cooling air introduction passage 28, and the cooling air discharge passage 29 are formed continuously in a direction perpendicular to the drive shaft 13 (left-right direction in Figure 2).

[0026] The cooling air intake passage 28 is formed such that its width dimension (specifically, the width dimension parallel to the arrangement direction of the multiple cooling fins 20) is greater than the width dimension of the guide 26a of the duct 26, but smaller than the overall width dimension of the multiple cooling fins 20. This increases the flow rate of cooling air in the radially inner portion of the orbiting scroll 12 compared to the radially outer portion of the orbiting scroll 12, thereby improving the cooling performance of the radially inner portion of the orbiting scroll 12.

[0027] Here, the gap between the multiple cooling fins 20 and the inner wall of the cooling fin housing portion 27 of the casing 10 needs to be of a certain size to avoid interference between them, and tends to be larger than the cooling channels formed between the cooling fins 20. Therefore, in the comparative example described later, cooling air is more likely to flow into the aforementioned gap than into the cooling channels located outside the cooling air introduction passage 28 in the width direction of the cooling air introduction passage 28. Consequently, the flow rate of cooling air in the radially outer portion of the orbiting scroll 12 is significantly reduced, resulting in a problem where the cooling performance of the radially outer portion of the orbiting scroll 12 is significantly reduced.

[0028] The multiple cooling fins 20 of this embodiment have the following characteristics on one side in the width direction of the cooling air intake passage 28 (the upper side in Figures 2 and 3).

[0029] The multiple cooling fins 20 include the third (in other words, the nth) cooling fin 20a3 from the outside, located on one side and outside the cooling air intake passage 28 (upper side in Figures 2 and 3) in the width direction of the cooling air intake passage 28; the second (in other words, the (n-1)th) cooling fin 20a2 from the outside, adjacent to the third cooling fin 20a3 on one side; the first (in other words, the (n-2)th) cooling fin 20a1 from the outside, adjacent to the second cooling fin 20a2 on one side; and the fourth (in other words, the (n+1)th) cooling fin 20a4 from the outside, adjacent to the third cooling fin 20a3 on the opposite side (lower side in Figures 2 and 3). Note that the third cooling fin 20a3 is located outside the cooling air intake passage 28 for the entire range of the rotation angle of the orbiting scroll 12 or only within a predetermined range.

[0030] To solve the aforementioned problems, the leading edge of the third cooling fin 20a3 is positioned downstream of the virtual straight line C1 connecting the leading edge of the second cooling fin 20a2 and the leading edge of the fourth cooling fin 20a4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air introduction passage 28 (to the right in Figures 2 and 3), the leading edge of the second cooling fin 20a2 is in the same position as the leading edge of the third cooling fin 20a3, and the leading edge of the fourth cooling fin 20a4 is positioned upstream of the leading edge of the third cooling fin 20a3.

[0031] Furthermore, the leading edge of the second cooling fin 20a2 is located downstream of the virtual straight line C2 connecting the leading edge of the first cooling fin 20a1 and the leading edge of the fourth cooling fin 20a4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air introduction passage 28, the leading edge of the first cooling fin 20a1 is in the same position as the leading edge of the third cooling fin 20a3.

[0032] The first, second, and third cooling fins 20a1, 20a2, and 20a3 each have an upstream portion and a downstream portion, separated by a boundary line L that passes through the radial center of the base plate 18 of the orbiting scroll 12 and is parallel to the width direction of the cooling air intake passage 28. The upstream portions of the first, second, and third cooling fins 20a1, 20a2, and 20a3 do not have screw holes into which screws for fixing the plate 21 are screwed, and their width is constant. The downstream portions of the second and third cooling fins 20a2 and 20a3 are longer than their upstream portions.

[0033] The multiple cooling fins 20 of this embodiment also have the following features on the opposite side of the cooling air intake passage 28 in the width direction (the lower side in Figure 2).

[0034] The multiple cooling fins 20 include the third cooling fin 20b3 from the outside (in other words, the mth fin) located on the opposite side and outside the cooling air intake passage 28 (lower side in Figure 2) in the width direction of the cooling air intake passage 28, the second cooling fin 20b2 from the outside (in other words, the (m-1)th fin) adjacent to the third cooling fin 20b3 on the opposite side, the first cooling fin 20b1 from the outside (in other words, the (m-2)th fin) adjacent to the second cooling fin 20b2 on the opposite side, and the fourth cooling fin 20b4 from the outside (in other words, the (m+1)th fin) adjacent to the third cooling fin 20b3 on one side (upper side in Figure 2). Note that the third cooling fin 20b3 is located outside the cooling air intake passage 28 for the entire range of the rotation angle of the orbiting scroll 12 or only within a predetermined range.

[0035] To solve the aforementioned problems, the leading edge of the third cooling fin 20b3 is positioned downstream of a hypothetical straight line connecting the leading edge of the second cooling fin 20b2 and the leading edge of the fourth cooling fin 20b4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air introduction passage 28, the leading edge of the second cooling fin 20b2 is in the same position as the leading edge of the third cooling fin 20b3, and the leading edge of the fourth cooling fin 20b4 is positioned upstream of the leading edge of the third cooling fin 20b3.

[0036] Furthermore, the leading edge of the second cooling fin 20b2 is located downstream of the imaginary straight line connecting the leading edge of the first cooling fin 20b1 and the leading edge of the fourth cooling fin 20b4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air intake passage 28, the leading edge of the first cooling fin 20b1 is in the same position as the leading edge of the third cooling fin 20b3.

[0037] The first, second, and third cooling fins 20b1, 20b2, and 20b3 each have an upstream portion and a downstream portion, separated by a boundary line L that passes through the radial center of the base plate 18 of the orbiting scroll 12 and is parallel to the width direction of the cooling air intake passage 28. The upstream portions of the first, second, and third cooling fins 20b1, 20b2, and 20b3 do not form screw holes into which screws that fix the plate 21 are screwed, and their width is constant. The downstream portions of the second and third cooling fins 20b2 and 20b3 are longer than their upstream portions.

[0038] Next, the effects of this embodiment will be explained using a comparative example. Figure 4 corresponds to Figure 3 and is a partially enlarged view showing the position of the leading edge of the cooling fins arranged on one side in the width direction of the cooling air intake passage in the comparative example.

[0039] The comparative example's multiple cooling fins include a third cooling fin 30a3 from the outside, located on one side in the width direction of the cooling air intake passage 28 (upper side of Figure 4), on the outside of the cooling air intake passage 28 (upper side of Figure 4); a second cooling fin 30a2 from the outside, adjacent to the third cooling fin 30a3 on one side; a first cooling fin 30a1 from the outside, adjacent to the second cooling fin 30a2 on one side; and a fourth cooling fin 30a4 from the outside, adjacent to the third cooling fin 30a3 on the opposite side (lower side of Figure 4).

[0040] The leading edges of the cooling fins 30a1 to 30a4 are located at the edges of the base plate 18. Therefore, the leading edge of the third cooling fin 30a3 is located upstream of the imaginary line connecting the leading edge of the second cooling fin 30a2 and the leading edge of the fourth cooling fin 30a4. The leading edge of the second cooling fin 30a2 is located upstream of the imaginary line connecting the leading edge of the first cooling fin 30a1 and the leading edge of the fourth cooling fin 30a4.

[0041] In this comparative example, the gap between the multiple cooling fins 30a1 to 30a4 and the inner wall of the cooling fin housing portion 27 of the casing 10 is larger than the cooling channels formed between the cooling fins 30a1 to 30a4. Therefore, cooling air flows more easily into the aforementioned gap than into the cooling channels formed between the cooling fins 30a1 to 30a4 (see the dotted arrow in Figure 4). Consequently, the flow rate of cooling air in the radially outer portion of the orbiting scroll 12 is significantly reduced, and the cooling performance of the radially outer portion of the orbiting scroll 12 is significantly reduced. As a result, the suction flow rate of the compressor decreases.

[0042] On the other hand, in this embodiment, on one side in the width direction of the cooling air introduction passage 28, the front edge of the third cooling fin 20a3 is positioned downstream of the imaginary straight line connecting the front edge of the second cooling fin 20a2 and the front edge of the fourth cooling fin 20a4. This creates an upstream expanding flow path for the cooling channel formed between the fourth cooling fin 20a4 and the third cooling fin 20a3, and for the cooling channel formed between the third cooling fin 20a3 and the second cooling fin 20a2. Also, the front edge of the second cooling fin 20a2 is positioned downstream of the imaginary straight line connecting the front edge of the first cooling fin 20a1 and the front edge of the fourth cooling fin 20a4. This creates an upstream expanding flow path for the cooling channel formed between the second cooling fin 20a2 and the first cooling fin 20a1. The presence of the upstream expanding flow path makes it easier for cooling air to flow into the cooling channel.

[0043] Furthermore, in this embodiment, on the opposite side of the width direction of the cooling air introduction passage 28, the leading edge of the third cooling fin 20b3 is positioned downstream of the imaginary straight line connecting the leading edge of the second cooling fin 20b2 and the leading edge of the fourth cooling fin 20b4. This creates an upstream expanding flow path for the cooling channel formed between the fourth cooling fin 20b4 and the third cooling fin 20b3, and for the cooling channel formed between the third cooling fin 20b3 and the second cooling fin 20b2. Also, the leading edge of the second cooling fin 20b2 is positioned downstream of the imaginary straight line connecting the leading edge of the first cooling fin 20b1 and the leading edge of the fourth cooling fin 20b4. This creates an upstream expanding flow path for the cooling channel formed between the second cooling fin 20b2 and the first cooling fin 20b1. The presence of the upstream expanding flow path makes it easier for cooling air to flow into the cooling channel.

[0044] Therefore, in this embodiment, the decrease in the flow rate of cooling air in the radially outer portion of the orbiting scroll 12 can be suppressed, and the decrease in the cooling performance of the radially outer portion of the orbiting scroll 12 can be suppressed. As a result, the decrease in the suction flow rate of the compressor can be suppressed.

[0045] In the above embodiment, the example given was that, in the flow direction of the cooling air perpendicular to the width direction of the cooling air intake passage, the leading edge of the nth cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-1)th cooling fin and the leading edge of the (n+1)th cooling fin, and furthermore, the leading edge of the (n-1)th cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-2)th cooling fin and the leading edge of the (n+1)th cooling fin. However, the embodiment is not limited to this. The leading edge of the (n-1)th cooling fin does not have to be located downstream of the imaginary straight line connecting the leading edge of the (n-2)th cooling fin and the leading edge of the (n+1)th cooling fin.

[0046] Furthermore, in the above embodiment, the case in which the leading edge of the (n-1)th cooling fin is at the same position as the leading edge of the nth cooling fin in the cooling air flow direction perpendicular to the width direction of the cooling air intake passage, and the leading edge of the (n+1)th cooling fin is located upstream of the leading edge of the nth cooling fin, was described as an example, but the invention is not limited to this. For example, in the cooling air flow direction perpendicular to the width direction of the cooling air intake passage, the leading edge of the (n-1)th cooling fin may be located upstream of the leading edge of the nth cooling fin, and the leading edge of the (n+1)th cooling fin may also be located upstream of the leading edge of the nth cooling fin. Such modifications will be explained using Figures 5 and 6.

[0047] Figure 5 is a radial cross-sectional view showing the structure of the cooling fins of the orbiting scroll in this modified example. Figure 6 is a partially enlarged view of part VI of Figure 5, showing the position of the leading edge of the cooling fins located on one side in the width direction of the cooling air intake passage. In this modified example, parts equivalent to those in the above embodiment are denoted by the same reference numerals, and their descriptions are omitted as appropriate.

[0048] In this modified example, on one side of the width direction of the cooling air inlet passage 28 (the upper side in Figures 5 and 6), the leading edge of the third cooling fin 20a3 is located downstream of the virtual straight line C1 connecting the leading edge of the second cooling fin 20a2 and the leading edge of the fourth cooling fin 20a4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air inlet passage 28 (the right direction in Figures 5 and 6), the leading edge of the second cooling fin 20a2 is located upstream of the leading edge of the third cooling fin 20a3, and the leading edge of the fourth cooling fin 20a4 is also located upstream of the leading edge of the third cooling fin 20a3. This creates an upstream expansion channel for the cooling channel formed between the fourth cooling fin 20a4 and the third cooling fin 20a3, and between the third cooling fin 20a3 and the second cooling fin 20a2. The presence of the upstream expansion channel makes it easier for cooling air to flow into the cooling channel.

[0049] Furthermore, in this modified example, on the opposite side of the width direction of the cooling air inlet passage 28 (the lower side of Figure 5), the leading edge of the third cooling fin 20b3 is located downstream of the imaginary straight line connecting the leading edge of the second cooling fin 20b2 and the leading edge of the fourth cooling fin 20b4. More specifically, in the direction of cooling air flow perpendicular to the width direction of the cooling air inlet passage 28, the leading edge of the second cooling fin 20b2 is located upstream of the leading edge of the third cooling fin 20b3, and the leading edge of the fourth cooling fin 20b4 is also located upstream of the leading edge of the third cooling fin 20b3. This creates an upstream expansion channel for the cooling channel formed between the fourth cooling fin 20b4 and the third cooling fin 20b3, and between the third cooling fin 20b3 and the second cooling fin 20b2. The presence of the upstream expansion channel makes it easier for cooling air to flow into the cooling channel.

[0050] Therefore, even in this modified configuration, the decrease in the flow rate of cooling air in the radially outer portion of the orbiting scroll 12 can be suppressed, and the decrease in the cooling performance of the radially outer portion of the orbiting scroll 12 can be suppressed. As a result, the decrease in the suction flow rate of the compressor can be suppressed. [Explanation of Symbols]

[0051] 11...Fixed scroll, 12...Swivel scroll, 13...Drive shaft, 15...Lap, 18...Base plate, 19...Lap, 20...Cooling fins, 25...Cooling fan, 28...Cooling air intake

Claims

1. A fixed scroll having a spiral wrap, A rotating scroll having a base plate, a spiral wrap erected on one side of the base plate, and a plurality of cooling fins erected on the opposite side of the base plate, A drive shaft for rotating the rotating scroll relative to the fixed scroll, A cooling fan that generates cooling air, The system includes a cooling air introduction path that introduces the cooling air generated by the cooling fan around the plurality of cooling fins, In a scroll compressor in which a plurality of working chambers are formed between the wrap of the fixed scroll and the wrap of the orbiting scroll, The aforementioned multiple cooling fins are In the width direction of the cooling air inlet passage, which is parallel to the arrangement direction of the cooling fins, the nth cooling fin is located on one side and outside the cooling air inlet passage, With respect to the nth cooling fin, the (n-1)th cooling fin adjacent to the one side thereof, The (n+1)th cooling fin adjacent to the nth cooling fin on the opposite side, Includes the (n-1)th cooling fin and an (n-2) cooling fin adjacent to the one side thereof, The leading edge of the nth cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-1)th cooling fin and the leading edge of the (n+1)th cooling fin. A scroll compressor characterized in that the leading edge of the (n-1)th cooling fin is located downstream of a virtual straight line connecting the leading edge of the (n-2)th cooling fin and the leading edge of the (n+1)th cooling fin.

2. In the scroll compressor according to claim 1, A scroll compressor characterized in that, in the flow direction of the cooling air perpendicular to the width direction of the cooling air intake passage, the leading edges of the (n-2)th and (n-1)th cooling fins are at the same position relative to the leading edge of the nth cooling fin, and the leading edge of the (n+1)th cooling fin is located upstream of the leading edge of the nth cooling fin.

3. A fixed scroll having a spiral wrap, A rotating scroll having a base plate, a spiral wrap erected on one side of the base plate, and a plurality of cooling fins erected on the opposite side of the base plate, A drive shaft for rotating the rotating scroll relative to the fixed scroll, A cooling fan that generates cooling air, The system includes a cooling air introduction path that introduces the cooling air generated by the cooling fan around the plurality of cooling fins, In a scroll compressor in which a plurality of working chambers are formed between the wrap of the fixed scroll and the wrap of the orbiting scroll, The aforementioned multiple cooling fins are In the width direction of the cooling air inlet passage, which is parallel to the arrangement direction of the cooling fins, the nth cooling fin is located on one side and outside the cooling air inlet passage, With respect to the nth cooling fin, the (n-1)th cooling fin adjacent to the one side thereof, Includes the (n+1)th cooling fin adjacent to the nth cooling fin on the opposite side, The leading edge of the nth cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-1)th cooling fin and the leading edge of the (n+1)th cooling fin. A scroll compressor characterized in that, in the flow direction of the cooling air perpendicular to the width direction of the cooling air intake passage, the leading edge of the (n-1)th cooling fin is at the same position as the leading edge of the nth cooling fin, and the leading edge of the (n+1)th cooling fin is located upstream of the leading edge of the nth cooling fin.

4. A fixed scroll having a spiral wrap, A rotating scroll having a base plate, a spiral wrap erected on one side of the base plate, and a plurality of cooling fins erected on the opposite side of the base plate, A drive shaft for rotating the rotating scroll relative to the fixed scroll, A cooling fan that generates cooling air, The system includes a cooling air introduction path that introduces the cooling air generated by the cooling fan around the plurality of cooling fins, In a scroll compressor in which a plurality of working chambers are formed between the wrap of the fixed scroll and the wrap of the orbiting scroll, The aforementioned multiple cooling fins are In the width direction of the cooling air inlet passage, which is parallel to the arrangement direction of the cooling fins, the nth cooling fin is located on one side and outside the cooling air inlet passage, With respect to the nth cooling fin, the (n-1)th cooling fin adjacent to the one side thereof, Includes the (n+1)th cooling fin adjacent to the nth cooling fin on the opposite side, The leading edge of the nth cooling fin is located downstream of the imaginary straight line connecting the leading edge of the (n-1)th cooling fin and the leading edge of the (n+1)th cooling fin. The nth cooling fin has an upstream portion and a downstream portion, distinguished by a boundary line that passes through the radial center of the base plate of the orbiting scroll and is parallel to the width direction of the cooling air intake passage, and the downstream portion is longer than the upstream portion, characterized in that the downstream portion is longer than the upstream portion.

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