JP2016035204A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent reduction of reliability due to abnormal wear and vibration generated by repeating a state (detachment) in which an end plate of an orbiting scroll is not always covered on an inner wall outermost circumferential portion of a fixed scroll in a view from a rotational axis direction.SOLUTION: Provided is a scroll compressor including a partition plate provided in a hermetic container; a compression element including a fixed scroll and an orbiting scroll in a low pressure chamber separated by the partition plate; and an electrical element driving this orbiting scroll to orbit, and configured so that a convex portion is provided so as to increase part of an end plate outside diameter of the orbiting scroll to outward of the outside diameter, and so that an end plate of the orbiting scroll always covers an inner wall outermost circumferential portion of the fixed scroll in a view from a rotational axis direction while the compression element (orbiting scroll) is driven to orbit.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a scroll compressor.

  In recent years, a partition plate is provided in a compression vessel, and a compression element having a fixed scroll and a turning scroll in a low-pressure side chamber partitioned by the partition plate and an electric element that drives the turning scroll to turn are sealed. A type scroll compressor is known. In this type of hermetic scroll compressor, the fixed scroll boss is fitted in the holding hole of the partition plate, and the refrigerant compressed by the compression element is separated by the partition plate through the discharge port of the fixed scroll. The thing provided with the structure discharged to the chamber of the side is proposed (for example, refer patent document 1).

  In the scroll compressor represented by Patent Document 1, since the periphery of the compression element is a low pressure space, the compression chamber formed by the orbiting scroll and the fixed scroll is compressed and discharged immediately after the suction confinement is completed. It is only necessary to be isolated from the low-pressure space in the compression container until the completion of the stroke, and before the suction confinement, the end plate of the orbiting scroll always covers the outer peripheral part of the inner wall of the fixed scroll as viewed from the direction of the rotation axis. Even if it is in a state of communicating with the low-pressure space without being configured, it can be established as a compression mechanism.

JP 11-182463 A

  However, in the scroll compressor having the above-described configuration, the end plate of the orbiting scroll is not always covered (dropped) when viewed from the rotation axis direction with respect to the outermost peripheral portion of the inner wall of the fixed scroll. Due to the bending or falling, a contact between the end plate edge portion of the orbiting scroll and the outermost peripheral portion of the inner wall of the fixed scroll occurs, and there is a problem of lowering reliability such as abnormal wear and vibration due to metal fatigue.

  Accordingly, the present invention provides a partition plate provided in an airtight container, a compression element having a fixed scroll and a turning scroll in a low-pressure side chamber partitioned by the partition plate, and an electric element for driving the turning scroll to turn. And a convex portion is provided so as to expand a part of the outer diameter of the end plate of the orbiting scroll to the outside of the outer diameter, and the end plate of the orbiting scroll is rotated while the compression element (orbiting scroll) is driven to rotate. Provided is a scroll compressor configured to always cover the inner wall outermost peripheral portion when viewed from the direction of the rotation axis, that is, the contour line of the edge portion of the end plate of the orbiting scroll always exceeds the inner wall outermost peripheral portion of the fixed scroll. .

  In the scroll compressor of the present invention, the outermost peripheral portion of the inner wall of the fixed scroll and the end plate edge portion of the orbiting scroll do not come into contact with each other, so that a stable driving state can always be maintained, and high reliability can be realized.

The longitudinal cross-sectional view of the scroll compressor which concerns on 1st Embodiment of this invention. (A) is a side view of the turning scroll used for the scroll compressor shown in FIG. 1, (b) is sectional drawing along XX in FIG. 2 (a) of a turning scroll. The bottom view of the fixed scroll used for the scroll compressor shown in FIG. (A)-(d) is the combination figure which shows the relative position of the turning scroll and fixed scroll in each rotation angle of the scroll compressor shown in FIG. Top view of the Oldham ring used in the scroll compressor shown in FIG.

  A first aspect of the present disclosure includes a partition plate provided in an airtight container, a compression element having a fixed scroll and a turning scroll in a low-pressure side chamber partitioned by the partition plate, and an electric motor that drives the turning scroll to turn. And a convex portion is provided so that a part of the outer diameter of the end plate of the orbiting scroll is widened outward, and the end plate of the orbiting scroll is fixed while the compression element (orbiting scroll) is driven to rotate. Provided is a scroll compressor configured to always cover the outermost peripheral part of the inner wall of the scroll when viewed from the rotational axis direction, that is, the contour line of the edge part of the end plate of the orbiting scroll always exceeds the outermost peripheral part of the inner wall of the fixed scroll. To do. With such a configuration, the outermost peripheral portion of the inner wall of the fixed scroll and the end plate edge portion of the orbiting scroll do not come into contact with each other, so that a stable driving state can always be maintained, and high reliability can be realized.

  According to a second aspect of the present disclosure, in addition to the first aspect, an inner wall of the spiral wrap of the fixed scroll is formed near the outer wall end of the spiral wrap of the orbiting scroll, and the compression element is engaged with the second wall. A scroll compressor is provided in which the confinement volumes of the two compression chambers are different. Such a configuration can increase the suction confinement volume without increasing the diameter of the compressor element, which is desirable from the viewpoint of downsizing the scroll compressor.

  In addition to the first or second aspect, the third aspect of the present disclosure is installed in parallel to the end plate surface of the orbiting scroll, and allows the orbiting motion to rotate with respect to the fixed scroll while preventing the orbiting scroll from rotating. Provided between the fixed scroll and a first engaging means that is provided between the rotation preventing mechanism and the orbiting scroll and that can reciprocate only in a first radial direction. And a second engagement means capable of reciprocating only in a second radial direction having an angle substantially perpendicular to the first radial direction, wherein the first engagement means is disposed on the orbiting scroll end plate. A pair of first radial key grooves (first key grooves) provided and a pair of first key grooves that are inserted and fitted in the first key grooves and slide along the first key grooves. The second engagement means is a fixed scroll. A pair of second radial key grooves (second key grooves) and a pair of second keys that are inserted and fitted into the second key grooves and slide along the second key grooves. And a scroll compressor in which the anti-rotation mechanism is disposed on the opposite side of the fixed scroll with respect to the orbiting scroll. According to such a configuration, when the Oldham ring is used as the rotation prevention mechanism, the first key and the second key provided on the Oldham ring are both arranged in the same plane direction of the Oldham ring. The number of times the Oldham ring is detached from the processing apparatus during ring processing is reduced, which is desirable from the viewpoint of improving processing accuracy and reducing processing costs.

  In the fourth aspect of the present disclosure, in addition to the third aspect, a virtual intersection of a first virtual line connecting the pair of first keys and a second virtual line connecting the pair of second keys is A scroll compressor that is offset with respect to the midpoint of the second imaginary line is provided. Such a structure can increase the extension angle of the spiral wraps of the orbiting scroll and the fixed scroll, so that it is easy to increase the compression ratio and volume, and is desirable from the viewpoint of high efficiency and downsizing of the scroll compressor.

According to a fifth aspect of the present disclosure, in addition to the first to fourth aspects, the spiral wrap of the orbiting scroll and the spiral wrap of the fixed scroll are provided at the end of each end plate from the beginning of the spiral wrap located at the approximate center of each end plate. Provided is a scroll compressor that is formed so that the thickness of the inner and outer walls of the spiral wrap gradually decreases toward the end of the spiral wrap positioned on the outer peripheral side. According to such a configuration, it is possible to achieve high efficiency and downsizing with high reliability by reducing the weight of the compression element and increasing the compression ratio and volume.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by the following embodiment.

(First embodiment)
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a configuration of a hermetic scroll compressor 100 according to the present embodiment. As shown in FIG. 1, the hermetic scroll compressor 100 includes a hermetic container 10 formed in a cylindrical shape extending in the vertical direction, and the upper part of the hermetic container 10 includes the inner part of the hermetic container 10. A partition plate 11 for partitioning up and down is provided. Inside the sealed container 10, the upper side of the partition plate 11 is a high pressure side space (high pressure side chamber) 12, and the lower side of the partition plate 11 is a low pressure side space (low pressure side chamber) 13.

  A compression element 14 that compresses the refrigerant and an electric element 15 that drives the compression element 14 are disposed in the low-pressure side space 13. The bottom of the low-pressure side space 13 is filled with lubricating oil that lubricates the compression element 14 and the like. The oil reservoir 16 is stored. The sealed container 10 includes a refrigerant suction pipe 17 that introduces a refrigerant into the low-pressure side space 13, and a refrigerant discharge pipe 18 that discharges the refrigerant compressed by the compression element 14 to the outside through the high-pressure side space 12. Is formed.

  The compression element 14 includes a fixed scroll 19 and an orbiting scroll 20, and the spiral scrolls 32 and 39 (described later) of the fixed scroll 19 and the orbiting scroll 20 are engaged with each other to form a plurality of compression spaces 21 inside. doing. The fixed scroll 19 includes a disk-shaped fixed scroll end plate 31, a spiral spiral wrap 32 erected on the lower surface of the fixed scroll end plate 31, and a peripheral wall 33 erected so as to surround the spiral wrap 32. And a flange 34 provided around the peripheral wall 33, and a discharge port 35 is formed at a substantially central portion of the fixed scroll end plate 31. In this configuration, the fixed scroll end plate 31 of the fixed scroll 19 protrudes to the upper surface side of the fixed scroll end plate 31 and includes a cylindrical protrusion (boss portion) 36 having a discharge port 35. The protrusion 36 is fitted into a holding hole 37 formed in the partition plate 11 so that the upper surface of the protrusion 36 faces the high-pressure side space 12. Further, the orbiting scroll 20 includes a disc-like orbiting scroll end plate 38 and a spiral wrap 39 standing on the upper surface of the orbiting scroll end plate 38 and formed so as to mesh with the spiral wrap 32 of the fixed scroll 19. A cylindrical boss 40 is formed substantially at the center of the lower surface of the orbiting scroll end plate 38.

  A main bearing 22 that supports the fixed scroll 19 and the orbiting scroll 20 is provided below the fixed scroll 19 and the orbiting scroll 20. The main bearing 22 is formed with a bearing portion 41 that pivotally supports the rotary shaft 23 that pivotally drives the orbiting scroll 20 and a boss accommodating portion 42 that accommodates the boss 40 of the orbiting scroll 20 at the substantially center thereof. Yes. An eccentric shaft 23 a that is eccentric with respect to the rotating shaft 23 is formed at the upper end of the rotating shaft 23, and this eccentric shaft 23 a can be driven to turn on the boss 40 via a swing bush 43 and a turning bearing 49. Has been inserted.

  In addition, the fixed scroll 19 is fixed to the main bearing 22 through a bolt penetrating portion 34 a using a plurality of bolts 24 at the flange 34 of the fixed scroll 19, while the orbiting scroll 20 is connected via the Oldham ring 25. It is supported by the fixed scroll 19. As a result, the orbiting scroll 20 is formed so as to orbit with respect to the fixed scroll 19 without rotating.

  The electric element 15 includes a stator 26 fixed to the hermetic container 10 and a rotor 27 disposed inside the stator 26, and the rotating shaft 23 is fixed to the rotor 27. A balance weight 55 is attached to the rotating shaft 23 in a positional relationship (a positional relationship of approximately 180 ° when viewed from the axial direction of the rotating shaft 23) on the upper and lower sides with the rotor 27 interposed therebetween. The balance weight 55 is for balancing the centrifugal force generated by the revolving motion of the orbiting scroll 20. A lower end 23 b of the rotating shaft 23 is pivotally supported by a sub-bearing 28 disposed at the bottom of the sealed container 10. In this configuration, in order to supply lubricating oil to the compression element 14 and the bearings 28, 41, 49 of the rotating shaft 23, an oil passage 44 through which the lubricating oil passes is formed inside the rotating shaft 23. The oil passage 44 includes a lubricating oil suction port 45 at the lower end of the rotating shaft 23 and a paddle 46 formed at the upper portion of the suction port 45, and is formed along the axial direction of the rotating shaft 23. The oil passage 44 is provided with an oil supply port 47 for supplying lubricating oil at a position corresponding to each bearing.

  When the rotating shaft 23 rotates, the lubricating oil accumulated in the oil reservoir 16 enters the oil passage 44 through the suction port 45 of the rotating shaft 23 and is pumped upward along the paddle 46 of the oil passage 44. The pumped lubricating oil lubricates the bearings 28, 41, and 49 through the oil supply ports 47. Further, the lubricating oil pumped up to the boss accommodating portion 42 is guided to the outer peripheral portion of the main bearing 22 through the return pipe 48 formed in the main bearing 22 and discharged from the discharge port 48a formed in the outer peripheral portion. As a result, the oil sump 16 is returned again.

  Fig.2 (a) is a side view of the turning scroll 20 in this embodiment, FIG.2 (b) is XX sectional drawing.

  A convex portion 38 b is provided on the outer peripheral portion of the orbiting scroll end plate 38. In FIG. 2 (b), the edge 38a on the end face side where the spiral wrap 39 is formed is indicated by a bold solid line among the outer peripheral edges of the orbiting scroll end plate 38 of the orbiting scroll 20 including the convex portion 38b. A first keyway 51 is formed in a part of the orbiting scroll end plate 38.

  FIG. 3 is a bottom view of the fixed scroll 19 in the present embodiment. In FIG. 3, the inner wall outermost peripheral portion 32a that is 360 ° from the end of the inner wall winding in the inner wall curve of the spiral wrap 32 of the fixed scroll 19 is indicated by a thick broken line.

  A suction part 29 for taking in the refrigerant into the compression element 14 is formed in a part of the peripheral wall 33 and the flange 34 of the fixed scroll 19, and a second keyway 50 is formed in a part of the flange 34. .

  FIG. 4 is a combination diagram showing the relative positions of the orbiting scroll 20 and the fixed scroll 19 at each rotation angle of the scroll compressor 100 in this embodiment.

  FIG. 4A shows a state in which the chamber A formed by the outer wall of the spiral wrap 39 of the orbiting scroll 20 and the inner wall of the spiral wrap 32 of the fixed scroll 19 is immediately after completion of the suction confinement.

  FIG. 4B shows a state where the 90 ° rotation has advanced from FIG.

  FIG. 4C shows a state in which the B chamber formed by the inner wall of the spiral wrap 39 of the orbiting scroll 20 and the outer wall of the spiral wrap 32 of the fixed scroll 19 is immediately after the suction is closed (FIG. 4). (A state where the rotation is advanced 180 ° from the state of (a))

  FIG. 4D shows a state where the rotation has further advanced by 90 ° from FIG.

  Among the rotation angles described above, the position where the orbiting scroll 20 is farthest from the suction portion 29 (near 180 °) is closest to the edge portion 38a of the orbiting scroll 20 and the outermost peripheral portion 32a of the inner wall of the fixed scroll 19. According to the scroll compressor 100 in the example, by providing the convex portion 38b so as to widen a part of the outer diameter of the orbiting scroll end plate 38 of the orbiting scroll 20 to the outside of the outer diameter, the orbiting scroll is operated while the orbiting scroll 20 is driven to orbit. 20 edge portions 38a always cover the inner wall outermost peripheral portion 32a of the fixed scroll 19 when viewed from the rotational axis direction, that is, the contour line of the edge portion of the end plate of the orbiting scroll always exceeds the outermost outer peripheral portion of the inner wall of the fixed scroll. be able to. For this reason, even when the orbiting scroll 20 bends or falls during operation, the inner wall outermost peripheral portion 32a of the fixed scroll 19 and the edge portion 38a of the orbiting scroll 20 do not come into contact with each other, and a stable driving state is always maintained. Can achieve high reliability.

  By the way, while providing the convex part 38b so that the outer diameter part of the orbiting scroll end plate 38 of the orbiting scroll 20 is widened outwardly, the edge part 38a of the orbiting scroll 20 is rotated while the compression element 14 is orbitally driven. As a configuration that can always cover the inner wall outermost peripheral portion 32 a of the fixed scroll 19 when viewed from the rotation axis direction, the extension angle at the end of the inner wall winding of the fixed scroll 19 is reduced, and the radial direction of the fixed scroll 19 is further reduced. A method for ending the inner wall at a position near the center of the end plate is raised. However, in this method, since the confining volume is reduced, it is necessary to design the swirl wraps 32 and 39 to have a large height in order to achieve an equivalent volume. There is a risk that a decrease in lap reliability, a decrease in rollover strength, a decrease in workability, and the like may occur. In addition, since the compression ratio also decreases, it becomes easy to cause insufficient compression, which may reduce the efficiency of the compressor.

  Further, even when the outer circumference of the orbiting scroll end plate 38 of the orbiting scroll 20 is increased, the edge portion 38a of the orbiting scroll 20 rotates the outermost peripheral portion 32a of the inner wall of the fixed scroll 19 while the compression element 14 is orbitally driven. The maximum outer diameter of the orbiting scroll end plate 38 of the orbiting scroll 20 can be always covered when viewed from the axial direction, but the orbiting scroll is formed on the bolt through portion 34 a that forms the fastening portion between the fixed scroll 19 and the main bearing 22. The design can be made only within a range where the end plate 38 does not contact. In order to increase the outer diameter of the orbiting scroll end plate 38 of the orbiting scroll 20, the bolt penetrating portion 34a is reduced and a bolt having a thinner nominal diameter is used. It is necessary to use it. For this reason, there is a possibility that problems such as poor mechanical fixing due to a decrease in rigidity of the fixed portion between the fixed scroll 19 and the main bearing 22 or a decrease in bolt tightening force may occur.

  For this reason, both high reliability and high efficiency can be achieved by the configuration of the scroll compressor 100 in the present embodiment.

  Further, the fixed scroll 19 and the orbiting scroll 20 in this embodiment form the inner wall of the spiral wrap 32 of the fixed scroll 19 to the vicinity of the outer wall winding end of the spiral wrap 39 of the orbiting scroll 20, and the compression element 14 is engaged. A configuration is employed in which the two compression chambers (A chamber and B chamber) formed have different confining volumes.

  Such a configuration can increase the suction confinement volume without increasing the diameter of the compression element 14, which is desirable from the viewpoint of downsizing the scroll compressor 100.

FIG. 5 is a top view of the Oldham ring 25 in the present embodiment. The Oldham ring 25 shown in FIG. 5 is formed with a first key 53 and a second key 52. The first key 53 is engaged with the first key groove 51 of the orbiting scroll 20, and the second key 52 is engaged with the second key groove 50 of the fixed scroll 19. Rotating motion is possible without rotating with respect to the fixed scroll 19. Further, as shown in FIG. 1, the fixed scroll 19, the orbiting scroll 20, and the Oldham ring 25 are arranged in this order from the top in the rotation axis direction.

  In order to arrange as shown in FIG. 1, the first key 53 and the second key 52 of the Oldham ring 25 are formed in the same plane direction of the ring portion 54. Therefore, when the Oldham ring 25 is processed, the first key 53 and the second key 52 can be processed from the same direction, and the number of times the Oldham ring 25 is detached from the processing apparatus can be reduced. It is possible to improve accuracy and reduce machining costs.

  Further, the Oldham ring 25 in FIG. 5 includes a virtual intersection O ′ between a first virtual line connecting the centers of the pair of first keys 53 and a second virtual line connecting the centers of the pair of second keys 52. Is offset by a distance L with respect to the midpoint O of the second imaginary line (the midpoint of the end portion in the radial direction of the second key 52). By adopting such a structure, the first key groove 51 of the orbiting scroll 20 can be offset from the center of the orbiting scroll end plate 38 as shown in FIG. Can be increased. As a result, since the outermost peripheral distance of the spiral wrap 39 can be increased from the center of the orbiting scroll end plate 38, the extension angle of the spiral wrap 39 can be designed to be large. For this reason, it is easy to increase the compression ratio and volume, and the scroll compressor can be made more efficient and smaller.

  Moreover, since the convex part 38b can be minimized by providing the convex part 38b in a position overlapping the suction part 29 in the axial direction as shown in FIG. 4, an effect of further weight reduction is obtained. I can do it.

  Further, the spiral wrap 39 of the orbiting scroll 20 shown in FIG. 2 and the spiral wrap 32 of the fixed scroll 19 shown in FIG. 3 gradually increase the thickness of the inner and outer walls of the spiral wrap from the beginning of winding of the spiral wrap (center of the end plate) to the end of winding. It is formed to be thin.

The inner and outer wall curves of the spiral wrap are represented by the following equation, for example, where the basic circle radius is a, the extension angle is θ, the turning radius is ε, B and n are coefficients,
xo = a · cos θ + (a · θ−B · θn) · sin θ (1) (outer wall X coordinate)
yo = a.sin.theta .- (a..theta.-B..theta.n) .cos .theta. (2) (outer wall Y coordinate)
xi = a · cos θ + (a · (θ−π) −B · (θ−π) n + ε) · sin θ (3) (inner wall X coordinate)
yi = a.sin.theta .- (a. (. theta .-. pi.)-B. (. theta .-. pi.) n + .epsilon.). cos .theta. (4) (inner wall Y coordinate)
And the coefficient B satisfies B> 0.

  According to such a configuration, the thickness at the end of winding of the spiral wrap can be reduced, so that the compression element 14 can be reduced in weight. In particular, the orbiting scroll can reduce the load on the bearing portion 41 and the orbiting bearing 49 due to the centrifugal force reduction effect during the orbiting drive due to the weight reduction, and the balance weight 55 provided on the rotating shaft 23 can be reduced in size. Therefore, the degree of freedom in design can be improved. Further, since the extension angle can be designed to be larger than that of the conventional spiral wrap shape, higher efficiency and smaller size can be realized by increasing the compression ratio and increasing the volume.

Moreover, in the above-described configuration, the thickness of the spiral wrap decreases as the spiral wrap ends, and the rigidity of the spiral wrap decreases, but this is combined with the configuration in which the convex portion 38b is formed on the orbiting scroll 20 as in the present embodiment. Therefore, it is possible to prevent the end edge portion 38a of the orbiting scroll 20 and the inner wall outermost peripheral portion 32a of the fixed scroll 19 from colliding with each other. As a result, both high performance and high reliability can be achieved.

  In this embodiment, the fixed scroll 19 is fixed to the main bearing 22 by the bolt 24. However, the fixed scroll is movable only in the direction of the rotation axis, and is pressed downward by the high pressure of the high-pressure side space 12. Needless to say, the same effect can be obtained by forming the convex portion 38b of the orbiting scroll 20 of this embodiment even in the case of the above configuration.

  INDUSTRIAL APPLICATION This invention is useful for the compressor of the refrigerating-cycle apparatus which can be utilized for electrical products, such as a water heater, a warm water heating apparatus, and an air conditioning apparatus.

DESCRIPTION OF SYMBOLS 10 Sealed container 11 Partition plate 12 High pressure side space 13 Low pressure side space 14 Compression element 15 Electric element 16 Oil reservoir 17 Refrigerant suction pipe 18 Refrigerant discharge pipe 19 Fixed scroll 20 Orbiting scroll 21 Compression space 22 Main bearing 23 Rotating shaft 24 Bolt 25 Oldham Ring 26 Stator 27 Rotor 28 Sub bearing 31 Fixed scroll end plate 32, 39 Spiral wrap 33 Peripheral wall 34 Flange 35 Discharge port 38 Orbiting scroll end plate

Claims (5)

A partition plate provided in the sealed container, a compression element having a fixed scroll and a turning scroll in a low-pressure chamber partitioned by the partition plate, and an electric element for driving the turning scroll to turn, the turning scroll A convex portion is provided so as to expand a part of the outer diameter of the end plate to the outside of the outer diameter, and the end plate of the orbiting scroll looks at the outermost peripheral portion of the inner wall of the fixed scroll from the direction of the rotation axis while the compression element is pivotally driven. A scroll compressor characterized by being configured so as to be always covered. The closed volume of the two compression chambers formed by forming the inner wall of the spiral wrap of the fixed scroll to the vicinity of the end of the outer wall of the spiral wrap of the orbiting scroll and the compression elements engaging with each other is different. The scroll compressor described. An anti-rotation mechanism installed parallel to the end plate surface of the orbiting scroll and allowing the orbiting scroll to rotate while preventing the orbiting scroll from rotating; and A first engaging means capable of reciprocating only in a first radial direction provided therebetween and a first radial direction provided between the fixed scroll and a second angle taking an angle substantially perpendicular to the first radial direction. And a second engagement means capable of reciprocating only in the radial direction, wherein the first engagement means is a first pair of key grooves in the radial direction (first key provided in the orbiting scroll end plate). Groove) and a pair of first keys that are inserted and fitted in the first key groove and slide along the first key groove, and the second engagement means is provided on the fixed scroll. A pair of second radial key grooves (second key ) And a pair of second keys that are inserted and fitted in the second key groove and slide along the second key groove, respectively, on the opposite side of the fixed scroll with respect to the orbiting scroll. The scroll compressor according to claim 1, wherein the rotation prevention mechanism is arranged. A virtual intersection of a first virtual line connecting the pair of first keys and a second virtual line connecting the pair of second keys is offset with respect to the midpoint of the second virtual line. The scroll compressor according to claim 3. The spiral wrap of the orbiting scroll and the spiral wrap of the fixed scroll are arranged from the beginning of the spiral wrap located substantially at the center of each end plate to the end of the spiral wrap located on the outer peripheral side of each end plate. The scroll compressor in any one of Claims 1-4 currently formed so that thickness may become thin gradually.

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