JP2016003634A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor capable of effectively cooling a central portion of each scroll.SOLUTION: A scroll compressor 1 comprises: a fixed scroll 20 including a lap 22 and a plurality of cooling fins 24; and an orbiting scroll 30 assembled so as to form a compression space for compressing a fluid between the fixed scroll 20 and the orbiting scroll 30, and including a lap 32 and a plurality of cooling fins 34. The fixed scroll 20 includes a first area α provided upstream in a flow direction of a cooling medium and coarse in a distribution of the cooling fins 24; and a second area β provided downstream of the first area α and denser in the distribution of the cooling fins 24 than the first area α.

Description

  The present invention relates to an improvement in cooling fins of a scroll compressor.

  The scroll compressor includes a fixed scroll and a turning scroll. Both the fixed scroll and the orbiting scroll are provided with a spiral wrap on one side of a disk-shaped end plate. Such a fixed scroll and the orbiting scroll are made to face each other in a state where the lap is engaged, and the orbiting scroll is caused to perform a revolving orbiting operation with respect to the fixed scroll. And the volume of the compression space formed between both scrolls is decreased with the turning of the orbiting scroll, thereby compressing the fluid in the space.

  In the scroll compressor, a large number of cooling fins are provided on the back of each of the end plate of the fixed scroll and the end plate of the orbiting scroll so as to dissipate the compression heat accompanying the compression of the fluid and the friction heat accompanying the rotation of each part. The thing is known (for example, patent document 1-patent document 4). In particular, in an oil-free scroll compressor that does not use refrigeration oil for lubrication, air cooling via cooling fins is employed.

Japanese Utility Model Publication No. 63-123788 Japanese Utility Model Publication No. 1-53485 JP 2002-257066 A JP 2010-84592 A

The scroll compressor draws in fluid to be compressed from the outer peripheral side of the scroll and gradually advances the compression toward the center. The compressed fluid is discharged to the outside from a port provided in the central portion of the fixed scroll. Since the temperature of the fluid increases as the degree of compression increases, the scroll is exposed to a higher temperature in the central portion. Therefore, the thermal expansion of the central part of the scroll is larger than the surrounding area, the sealing performance between the fixed scroll and the orbiting scroll is lowered and the compression efficiency is lowered, or the tip of the wrap is placed on the other end plate. There is a risk of seizing in close contact.
Then, an object of this invention is to provide the scroll compressor which can cool the center part of a scroll effectively.

  The scroll compressor according to the present invention, which is based on such a purpose, is a compression space for compressing fluid between a fixed scroll provided with a fixed wrap on the front and a plurality of fixed cooling fins on the back, and the fixed scroll. And a orbiting scroll provided with a swirl wrap on the front and a plurality of cooling fins on the back, and one or both of the fixed scroll and the orbiting scroll have a direction in which the cooling medium flows. A first region having a coarse distribution of cooling fins provided on the upstream side, and a second region having a distribution of cooling fins denser than that of the first region, provided on the downstream side of the first region. It is characterized by that.

  Since the temperature of the cooling medium increases on the downstream side in the direction in which the cooling medium flows, if the fin distribution is the same as that on the upstream side, the cooling efficiency is worse than that on the upstream side. In particular, the temperature of the cooling medium that has passed through the central portion where the temperature is high also increases, and the cooling efficiency on the downstream scroll outer periphery is lower than that on the upstream scroll outer periphery. Therefore, the scroll compressor according to the present invention is arranged on the downstream side including the center portion of the scroll by closely arranging the fin distribution in the second region provided downstream of the first region to increase the cooling efficiency. Efficiency can be made equal to the upstream side.

  In the scroll compressor according to the present invention, the second region is provided adjacent to the first region, the 2-1 region having a dense distribution of cooling fins, and the downstream side of the 2-1 region. It is preferable that the cooling fin distribution includes a 2-2 region that is coarser than the 2-1 region. By making the distribution of the cooling fins in the 2-1 region most dense and making the 2-1 region correspond to the central portion of the scroll, the central portion can be efficiently cooled.

  In the scroll compressor of the present invention, it is preferable that cooling fins are arranged in a staggered manner in the second region. Moreover, the scroll compressor of this invention WHEREIN: It is preferable that the 1st area | region has the fin arranged radially. Furthermore, the scroll compressor according to the present invention preferably includes a guide for guiding the supplied cooling medium to the second region. In any case, the central portion can be efficiently cooled.

  In the scroll compressor of the present invention, when the cooling fin belonging to the first region is shorter than the cooling fin belonging to the second region, the center portion of the scroll can be cooled more efficiently.

  According to the scroll compressor of the present invention, since the distribution of the cooling fins in the second region corresponding to the center portion of the scroll is made dense, the center portion of the scroll can be efficiently cooled.

It is a longitudinal cross-sectional view which shows the principal part of the scroll compressor which concerns on embodiment of this invention. It is a cross-sectional view of the rotation prevention mechanism of the scroll compressor of FIG. It is a top view which shows the fixed scroll which concerns on FIG. 1 from the back side. The fixed scroll which concerns on the modification of this embodiment is shown, (a) is a top view shown from the back side, (b) is a longitudinal cross-sectional view. It is a top view which shows the fixed scroll which concerns on the other modification of this embodiment from the back side. It is a top view which shows the fixed scroll which concerns on the other modification of this embodiment from the back side. The fixed scroll which concerns on the other modification of this embodiment is shown, (a) is a top view shown from the back side, (b) is a longitudinal cross-sectional view. It is a longitudinal cross-sectional view which shows the principal part which concerns on the other modification of this embodiment.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
As shown in FIG. 1, the scroll compressor 1 of the present embodiment is accommodated in a housing 10 that forms an outer shell of the scroll compressor 1, a fixed scroll 20 that is fixed to the housing 10, and a swivel inside the housing 10. The orbiting scroll 30 is provided as a main component. These main components are made of a metal material such as an aluminum alloy or an iron alloy.

[Housing 10]
As shown in FIG. 1, the housing 10 is a hermetic container including a first housing 10a and a second housing 10b.
The first housing 10 a is fixed to the fixed scroll 20 and accommodates the cooling fins 24 of the fixed scroll 20 inside. The first housing 10 a includes a discharge port 12 that discharges the compressed fluid discharged from the discharge port 21 e of the fixed scroll 20 toward the outside.
The second housing 10b houses and holds the orbiting scroll 30, the rotation prevention mechanism 40, and the drive shaft 50 in the housing chamber 11b. The second housing 10 b includes a storage chamber 11 c that stores the second element 45 of the rotation prevention mechanism 40 and a storage chamber 11 d that stores the drive shaft 50 and the main bearing 54 inside the storage chamber 11 b.

[Fixed scroll 20]
As shown in FIG. 1, the fixed scroll 20 includes an end plate 21 formed in a substantially disc shape, a spiral wrap 22 provided on one surface side of the end plate 21, and the other surface of the end plate 21. The cooling fin 24 provided on the side and the outer peripheral wall 26 surrounding the outermost periphery of the fixed scroll 20 are provided, and are integrally formed by casting, for example, an aluminum alloy. The outer peripheral wall 26 is provided with a suction port 27 for sucking a fluid to be compressed. Further, the outer peripheral wall 26 is exposed to the outside and constitutes a part of the housing 10. In the fixed scroll 20, the side on which the wrap 22 is provided is referred to as the front, and the side on which the cooling fins 24 are provided is referred to as the back. The tip of the wrap 22 is provided with a tip seal 23 having a self-lubricating property that contacts and seals the end plate 31 of the orbiting scroll 30.

  The end plate 21 is formed with a discharge port 21e penetrating the front and back, and the fluid compressed by the fixed scroll 20 and the orbiting scroll 30 is discharged from the discharge port 12 to the outside through the discharge port 21e.

  A plurality of cooling fins 24 are provided on the back surface of the end plate 21, and an air flow (hereinafter referred to as a cooling medium) supplied from a blower fan (not shown) passes between the cooling fins 24, thereby fixing the scroll. 20 is cooled. In the present embodiment, a plurality of flat plate-like cooling fins 24 are formed. However, for example, a corrugated cooling fin 24 or a pin-like cooling fin 24 can be used. . In addition to arranging all the cooling fins 24 in parallel in one direction, the cooling fins 24 can be partially arranged radially. The same applies to the orbiting scroll 30.

Further, as shown in FIG. 3, the cooling fin 24 is provided by dividing the back side of the end plate 21 into a first region α and a second region β. The first region α is disposed on the upstream side and the second region β is disposed on the downstream side of the first region α with reference to the cooling medium flow direction D indicated by the white arrow. The second region β includes the center C of the fixed scroll 20.
Here, the cooling fins 24 belonging to the upstream first region α are referred to as cooling fins 24α, and the cooling fins 24 belonging to the downstream second region β are referred to as cooling fins 24β. In the first region α, the long cooling fins 24α are arranged in parallel in a plurality of rows, whereas in the second region β, the cooling fins 24β shorter than the cooling fins 24α are arranged in a staggered manner. Yes. Moreover, in the second region β, the number of cooling fins 24β is larger than that in the first region α by making the interval (fin pitch) between adjacent cooling fins 24β narrower than that in the first region α. That is, the plurality of cooling fins 24β in the second region β is more densely distributed than the plurality of cooling fins 24α in the first region α. By adopting the distribution structure of the cooling fins 24α and the cooling fins 24β, the cooling efficiency of the second region β is higher than that of the first region α.

[Swivel scroll 30]
As shown in FIG. 1, the orbiting scroll 30 includes an end plate 31 formed in a substantially disc shape, a spiral wrap 32 provided on one surface side of the end plate 31, and the other surface of the end plate 31. The cooling fin 34 is provided on the side, and is integrally formed by casting, for example, an aluminum alloy. As with the fixed scroll 20, the side on which the wrap 32 is provided is referred to as the front surface, and the side on which the cooling fins 34 are provided is referred to as the back surface.

The wrap 32 of the orbiting scroll 30 has the same height as the wrap 22 of the fixed scroll 20.
The tip of the wrap 32 is provided with a tip seal 33 having a self-lubricating property that contacts the front side of the end plate 21 of the fixed scroll 20 and seals the compression chamber.

A plurality of cooling fins 34 are provided on the back surface of the end plate 31. Like the cooling fins 24 of the fixed scroll 20, the cooling medium to be supplied passes through the cooling fins 34 to cool the orbiting scroll 30. . The plurality of plate-like cooling fins 34 are formed in the same direction.
Similarly to the cooling fins 24 of the fixed scroll 20, the cooling fins 34 have a coarse distribution of the first region α disposed on the upstream side, and the second region disposed on the downstream side of the first region α. The distribution of β is dense.

The orbiting scroll 30 includes a bearing plate 35 that is fixed to the front end side of the cooling fin 34.
The bearing plate 35 includes a boss 36 that accommodates and fixes the bearing 37 in the central portion. The bearing 37 held by the boss 36 supports the eccentric shaft 53 of the drive shaft 50.
As shown in FIG. 2, the bearing plate 35 includes three bosses 38 that accommodate the first elements 41 of the rotation prevention mechanism 40 at equal intervals in the circumferential direction.

[Rotation prevention mechanism 40]
The rotation prevention mechanism 40 is a pin crank type rotation prevention mechanism, and includes a first element 41 and a second element 45 as shown in FIG. The scroll compressor 1 includes three rotation prevention mechanisms 40 corresponding to the three bosses 38.
The first element 41 includes a bearing 42. The bearing 42 includes, for example, a ball bearing including an inner ring, an outer ring, and a spherical rolling element provided between the inner ring and the outer ring. A crank pin 43 is fitted to the inner ring of the bearing 42 and constitutes the first element 41 together with the bearing 42. The first element 41 is accommodated in a boss 38 of the bearing plate 35, and this boss 38 functions as a bearing box of the bearing 42.
The second element 45 has the same configuration as the first element 41, and includes two bearings 46 and a crank pin 47 that is inserted into the inner ring of the bearing 46. The second element 45 is accommodated and held in the accommodation chamber 11 c of the housing 10.

  The crank pin 43 of the first element 41 and the crank pin 47 of the second element 45 are integrally connected via an eccentric shaft 44, and the crank pin 43, the crank pin 47 and the eccentric shaft 44 are integrated with each other. Configure.

  As shown in FIG. 2, the boss 38 has an inner wall 38 a, and the inner wall 38 a regulates the amount and direction of displacement of the bearing 42. Unlike the perfect circle, the opening of the inner wall 38a has an elliptical shape having a major axis in the radial direction and a minor axis in the circumferential direction. That is, the boss 38 and the bearing 42 have anisotropy that the allowable displacement amount of the bearing 42 (crank pin 47) is large in the radial direction and small in the circumferential direction. Therefore, even if the orbiting scroll 30 is thermally expanded, the displacement in the radial direction of the bearing 42 is absorbed, but the amount by which the bearing 42 is displaced in the circumferential direction can be kept small. Therefore, it is possible to suppress the turning scroll 30 from being twisted with respect to the fixed scroll 20.

[Drive shaft 50]
The drive shaft 50 transmits a rotational driving force of a driving source (not shown), for example, an electric motor, to the orbiting scroll 30.
As shown in FIG. 1, the drive shaft 50 has a connection end 51 connected to the drive source on one end side, and an eccentric shaft 53 held on a bearing 37 held on the bearing plate 35 on the other end. It has been.
The drive shaft 50 is rotatably supported on the housing 10 by two bearings of a main bearing 54 and a sub bearing 55. The main bearing 54 supports the drive shaft 50 in the vicinity of the eccentric shaft 53, and the auxiliary bearing 55 supports the drive shaft 50 in the vicinity of the connection end 51.

[Operation of scroll compressor 1]
Next, the operation of the scroll compressor 1 having the above configuration is as follows.
When the drive shaft 50 rotates according to the rotation of the drive source (not shown), the orbiting scroll 30 starts a revolving orbiting motion. Then, the fluid sucked from the suction port 27 is compressed in the crescent-shaped compression space formed by the wrap 22 and the wrap 32 and is discharged from the discharge port 12 provided in the central portion.
While the scroll compressor 1 is operating, the rotation prevention mechanism 40 prevents the orbiting scroll 30 from rotating.
Further, while the scroll compressor 1 is in operation, the outside air taken in through the cooling fins 24 provided on the back surface of the fixed scroll 20 and the cooling fins 34 provided on the back surface of the orbiting scroll 30 passes through the fixed scroll. 20 and the orbiting scroll 30 are cooled.

[Effect of scroll compressor 1]
Next, the effect of the scroll compressor 1 will be described.
Since the temperature rises when the fluid is compressed, the fixed scroll 20 and the orbiting scroll 30 are exposed to a high temperature and thermally expand while the scroll compressor 1 is operating. If the thermal expansion exceeds the allowable range, the tooth tip of one scroll and the tooth bottom of the other scroll come into contact with each other, and there is a concern that smooth orbiting motion of the orbiting scroll 30 may be hindered. Particularly, the central portion in the radial direction of the orbiting scroll 30 where the degree of compression increases is exposed to high temperatures.

However, since the fixed scroll 20 and the orbiting scroll 30 are cooled via the cooling fins 24 and the cooling fins 34, thermal expansion can be suppressed.
In particular, in the scroll compressor 1, as shown in FIG. 3, the plurality of cooling fins 24β in the second region β including the central portions of the fixed scroll 20 and the orbiting scroll 30 are more than the plurality of cooling fins 24α in the first region α. Since the second region β has a larger cooling area than the first region α, the cooling efficiency can be increased.
The coolant whose temperature has risen through the first region α flows into the second region β, which is the downstream side in the direction in which the coolant flows. Therefore, if the distribution density of the cooling fins 24β in the second region β and the cooling fins 24α in the first region α are the same, the cooling efficiency in the second region β is worse than that in the first region α. However, in the present embodiment, the cooling efficiency is increased by densely distributing the cooling fins 24β in the second region β, so that the cooling efficiency equivalent to that of the first region α can be obtained for the second region β.
In addition, since the plurality of cooling fins 24β in the second region β are arranged in a staggered manner, a leading edge effect is generated in each cooling fin 24β, so that the heat transfer coefficient is high. Therefore, the scroll compressor 1 has a great effect of suppressing the thermal expansion of the central portion, and the temperature distribution generated in the fixed scroll 20 and the orbiting scroll 30 is reduced.
Further, since the cooling medium that has passed through the first region α flows into the second region β, the cooling fin 24β in the second region β can be efficiently cooled as the temperature rise of the cooling medium in the first region α is smaller. it can. Since the first region α has a smaller temperature increase due to fluid compression than the central portion, a sufficient cooling effect can be obtained even if the distribution of the cooling fins 24α is coarser than that of the cooling fins 24β in the second region β. In addition, the temperature rise of the cooling medium can be minimized and thermal expansion of the central portion can be suppressed.

  In the embodiment described above, the configurations shown in FIGS. 4 to 8 can be employed in order to improve the cooling efficiency of the central portion. In the following, the fixed scroll 20 will be described, but the configuration described below can also be adopted for the orbiting scroll 30.

In the fixed scroll 20 shown in FIG. 4, the back of the cooling fin 24α belonging to the first region α is set lower than the cooling fin 24β belonging to the second region β, as shown in FIG. In this way, a part of the cooling medium supplied to the first region α is directly introduced into the second region β while the temperature that does not pass through the cooling fin 24α remains low. The fins 24β can be efficiently cooled. Thus, if the structure shown in FIG. 4 is adopted, the temperature distribution generated in the fixed scroll 20 and the orbiting scroll 30 can be further reduced.
In the form of FIG. 4, it is preferable to cover the fins 24α and 24β with the air passage cover 66 from above. By doing so, the cooling medium can be reliably guided to the cooling fins 24β in the second region β.

  In the fixed scroll 20 shown in FIG. 5, the cooling fins 24α belonging to the first region α are radially arranged. In this way, the cooling medium that has passed through the first region α can be easily guided to the central portion of the fixed scroll 20 in the second region β. Therefore, if the configuration shown in FIG. 5 is adopted, the temperature distribution generated in the fixed scroll 20 and the orbiting scroll 30 can be further reduced.

  In the fixed scroll 20 shown in FIG. 6, the second region β is divided into a 2-1 region β1 corresponding to the central portion of the scroll compressor 1 and a 2-2 region β2 occupying a region excluding the 2-1 region β1. The cooling fins 24β belonging to each of these are referred to as cooling fins 24β1 and cooling fins 24β2. The cooling fins 24β1 belonging to the 2-1 region β1 are constituted by cylindrical pin-shaped fins and have a denser distribution than the cooling fins 24β2 belonging to the 2-2 region β2. Therefore, if the configuration shown in FIG. 6 is adopted, the temperature distribution generated in the fixed scroll 20 and the orbiting scroll 30 can be further reduced.

The function of the fixed scroll 20 shown in FIG. 7 is the same as that of the embodiment shown in FIG. 4, and the temperature of the fixed scroll 20 is low without passing a part of the cooling medium supplied to the first region α through the cooling fins 24α. Until now, it is introduced directly into the second region β. For this purpose, the present embodiment provides a cover guide 60 that covers the cooling fin 24β from above.
The cover guide 60 includes an introduction plate 61, a connection portion 63 that is continuous with the introduction plate 61, and that is inclined with respect to the introduction plate 61, and a shielding plate 65 that is continuous with the connection portion 63 and is parallel to the introduction plate 61. .
Further, the cover guide 60 corresponds to the upstream side of the flow of the cooling medium corresponding to the first region α with the introduction plate 61, and the connecting portion 63 corresponds to the central portion of the scroll compressor 1 corresponding to the 2-1 region β1. The shielding plate 65 is formed so as to be arranged on the downstream side corresponding to the 2-2 region β2. The introduction plate 61 is provided at a predetermined interval from the tip of the cooling fin 24β1. The connecting portion 63 is provided so as to be inclined from a portion continuous with the introduction plate 61 toward a portion continuous with the shielding plate 65. Further, the shielding plate 65 shields the 2-2 region β2 by contacting the cooling fin 24β2.

As shown in FIG. 7, a part of the supplied cooling medium is introduced from the upstream end into the cooling fin 24α in the first region α, and the other part is connected to the introduction plate 61 without passing through the first region α. Guided in turn by the part 63 and introduced directly into the 2-1 region β1. Therefore, since the cooling medium having a low temperature is introduced into the central portion, the central portion can be efficiently cooled.
In the form shown in FIG. 7, it is preferable to cover the top surface of the cooling fin 24α in the first region α with the partition plate 67, thereby preventing the cooling medium from being introduced into the first region α from above. The cooling medium can be more reliably guided to the 2-1 region β1.

  In FIG. 8, the scroll compressor 1 is a so-called 3D in which the fixed side wrap and the turning side wrap are provided with steps at the tooth tip and the root, respectively, so that the outer peripheral side is taller than the inner side. A compressor called Scroll (registered trademark) is listed. The 3D scroll type compressor has a feature that a high compression ratio can be obtained by adopting a three-dimensional compression mechanism that compresses fluid not only in the circumferential direction but also in the height direction.

As shown in FIG. 8, the 3D type scroll compressor 1 includes a low step portion 21 a and a high step portion 21 b on the end plate 21 so that the height of the wrap 22 is lower on the inner peripheral side than on the outer peripheral side. The wrap 22 formed in the low step portion 21a is tall and the wrap 22 formed in the high step portion 21b is short. A step at the boundary between the low step portion 21a and the high step portion 21b also appears on the back surface of the end plate 21, and a concave groove 21c that surrounds the discharge port 12 and recedes toward the front is formed in this portion. Is done. Similarly, the orbiting scroll 30 is also provided with a low step portion 31a and a high step portion 31b on the end plate 31, and the wrap 32 formed on the low step portion 31a is tall and formed on the high step portion 31b. The wrap 32 is short. In FIG. 8, the same components as those in FIG. 1 are denoted by the same reference numerals as those in FIG.
According to the above-described embodiment, the cooling fins 24 of the fixed scroll 20 are distributed more densely than the cooling fins 24α in the first region α in the second region β including the central portion of the fixed scroll 20. It is said that. The distribution is the same for the cooling fins 34 of the orbiting scroll 30.

Also in the 3D type scroll compressor 1, based on the fact that the plurality of cooling fins 24β in the second region β is more densely distributed than the plurality of cooling fins 24α in the first region α, the thermal expansion of the central portion is performed. In addition to the suppressing effect, the following actions and effects are exhibited.
In the 3D type scroll compressor 1, the cooling fins 24 and the cooling fins 34 provided in the fixed scroll 20 and the orbiting scroll 30 where the temperature is high are higher in the center portion than in the surroundings, so that the cooling capacity is high.
Since the scroll compressor 1 is a 3D type scroll compressor, the back surface of the fixed scroll 20 and the back surface of the orbiting scroll 30 are both recessed in the lower stage portions 21a and 31a located in the center. In the present embodiment, the height of the cooling fins 24 and the cooling fins 34 of the portion is increased by using this recess. On the other hand, the tips of the cooling fins 24 are arranged on the same plane in the central portion and the peripheral portion around it. The same applies to the cooling fins 34. Therefore, the scroll compressor 1 can align the positions of the tips of the cooling fins 24 and 34 from the center to the outer periphery, while increasing the height of the cooling fins 24 and 34 in the center portion. This prevents the cooling fins 24, 34 located in the central portion from projecting to make the cooling fins 24, 34 tall, so as not to occupy unnecessary space around them. This suggests that a flat shape is sufficient for the portion corresponding to the cooling fins 24 of the first housing 10a.

  The preferred embodiments of the present invention have been described above. However, the configurations described in the above embodiments can be selected or changed to other configurations as appropriate without departing from the gist of the present invention. is there.

  For example, in the embodiment described above, an example in which the present invention is applied to both the cooling fins 24 of the fixed scroll 20 and the cooling fins 34 of the orbiting scroll 30 has been described. Only one of the two is allowed to be divided into the first region α and the second region β. The present invention can also be applied to the case where the cooling fin is provided only in one of the fixed scroll 20 and the orbiting scroll 30.

  In addition, the scroll compressor 1 is merely an example, and the present invention can be widely applied to a scroll compressor including cooling fins.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 10 Housing 10a 1st housing 10b 2nd housing 11b Storage chamber 11c Storage chamber 11d Storage chamber 12 Discharge port 20 Fixed scroll 21 End plate 21a Low step portion 31a Low step portion 21b High step portion 31b High step portion 21c Concave Groove 21e Discharge port 22 Lap 23 Chip seal 24 Cooling fin 24α Cooling fin 24β Cooling fin 24β1 Cooling fin 24β2 Cooling fin 26 Outer peripheral wall 27 Suction port 30 Revolving scroll 31 End plate 32 Lap 33 Chip seal 34 Cooling fin 35 Bearing plate 36 Boss 37 Bearing 38 Boss 38a Inner wall 40 Anti-rotation mechanism 41 First element 42 Bearing 43 Crank pin 44 Eccentric shaft 45 Second element 46 Bearing 47 Crank pin 50 Drive shaft 51 Connecting end 53 Eccentric shaft 54 Main bearing 55 Sub bearing 60 Cover guide 61 Guide Entrance plate 63 Connecting portion 65 Shielding plate 66 Air passage cover 67 Partition plate C Center α First region β Second region β1 2-1 region β2 Second 2-2 region

Claims (6)

A fixed scroll provided with a fixed side wrap on the front and a plurality of cooling fins on the back;
A revolving scroll that is combined with the fixed scroll so as to form a compression space for compressing fluid, and provided with a revolving wrap on the front and a plurality of cooling fins on the back,
One or both of the fixed scroll and the orbiting scroll are
A first region having a rough distribution of the cooling fins provided on the upstream side in a direction in which the cooling medium flows;
A second region having a distribution of the cooling fins denser than the first region, provided downstream of the first region;
A scroll compressor characterized by comprising: The second region is
A second region 2-1 having a dense distribution of the cooling fins provided adjacent to the first region;
The cooling fin distribution is provided on the downstream side of the 2-1 region, the 2-2 region is coarser than the 2-1 region,
The scroll compressor according to claim 1. The second region is
The cooling fins are arranged in a staggered manner,
The scroll compressor according to claim 1 or 2. The first region is
The fins are arranged radially,
The scroll compressor as described in any one of Claims 1-3. A guide for guiding the supplied cooling medium to the second region;
The scroll compressor as described in any one of Claims 1-4. The cooling fin belonging to the first region is
Shorter than the cooling fins belonging to the second region,
The scroll compressor as described in any one of Claims 1-5.

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