WO2014108973A1

WO2014108973A1 - Scroll compressor

Info

Publication number: WO2014108973A1
Application number: PCT/JP2013/007562
Authority: WO
Inventors: 雄司尾形; 山田　定幸; 悠介今井; 秀信新宅; 森本　敬; 淳作田
Original assignee: パナソニック株式会社
Priority date: 2013-01-09
Filing date: 2013-12-25
Publication date: 2014-07-17
Also published as: JP2016035204A

Abstract

[Problem] A situation occurs repeatedly wherein the end plate of the orbiting scroll, when viewed from the direction of the rotational axis, does not constantly cover (disengages from) the outermost circumferential part of the inner wall of the fixed scroll, resulting in abnormal wear and vibration, which reduces the reliability. [Solution] A scroll compressor wherein: the interior of a sealed container (10) is divided into a low-pressure space (13) and a high-pressure space (12) by a partition plate (11); a compression element (14) having a fixed scroll (19) and an orbiting scroll (20), and an electromotive element (15) that rotationally drives the orbiting scroll (20), are provided in the low-pressure space (13); a protruding part (38b), a portion of the end surface of which expands outward, is formed on an end plate (38) of the orbiting scroll; the fixed scroll (19) is equipped with a fixed spiral lap (32) erected on an end plate (31) of the fixed scroll; and when a fixed lap inner wall (32in), which is formed over an interval running 360° from the winding-end part (39b) of the fixed spiral lap (32), is set as the outermost circumferential part (32a) of the inner wall, the outermost circumferential part (32a) of the inner wall is constantly covered by the end surface of the orbiting scroll end plate (38) during rotational driving of the orbiting scroll.

Description

Scroll compressor

The present invention relates to a scroll compressor.

In recent years, a sealed type in which a partition plate is provided in a compression container, and a compression element having a fixed scroll and a turning scroll and an electric element for driving the turning scroll are arranged in a low-pressure chamber partitioned by the partition plate Scroll compressors are 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).

Scroll compressors represented by Patent Document 1 have a low pressure space around the compression element. Therefore, the compression chamber formed by the orbiting scroll and the fixed scroll only needs to be isolated from the low-pressure space in the compression container from the completion of the suction confinement, through the compression stroke, to the completion of the discharge stroke. Therefore, it is not necessary to always cover the outermost peripheral portion of the inner wall of the fixed scroll with the end plate of the orbiting scroll before the suction is closed, and the compression mechanism can be established even if the compression chamber is communicated with the low pressure space.

JP 11-182463 A

However, in the scroll compressor of Patent Document 1, a state in which the end plate of the orbiting scroll does not cover the outermost peripheral portion of the inner wall of the fixed scroll repeatedly occurs due to the orbiting drive. In a state in which the end plate of the orbiting scroll does not cover the outermost peripheral portion of the inner wall of the fixed scroll, the orbiting scroll may bend or fall down, so that the end portion of the end plate of the orbiting scroll and the outermost peripheral portion of the inner wall of the fixed scroll come into contact. Metal contact due to abnormal wear and vibration occurs due to the one-piece contact.

Therefore, the present invention provides a partition plate in a sealed container, and the partition plate divides the sealed container into a low pressure space and a high pressure space, and the compression element having a fixed scroll and a turning scroll in the low pressure space; And an electric element for driving the orbiting scroll to rotate. Forming a convex part in which a part of the end surface is expanded outward, and the fixed scroll includes a disk-shaped fixed scroll end plate and a fixed spiral wrap erected on the fixed scroll end plate, When the fixed wrap inner wall formed between 360 ° from the winding end of the fixed spiral wrap is the innermost wall outermost part, the innermost wall outermost part is swiveled. Dochu provides scroll compressor covered at all times by the end surface of the orbiting scroll end plate.

In the scroll compressor according to 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 orbiting scroll used in the scroll compressor shown in FIG. 1, and (b) is a cross-sectional view of the orbiting scroll taken along line XX in FIG. 2 (a). The bottom view of the fixed scroll used for the scroll compressor shown in FIG. (A)-(d) are the combination diagrams which show the relative position of a turning scroll and a 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.

According to a first aspect of the present disclosure, a partition plate is provided in a sealed container, and the sealed container is divided into a low-pressure space and a high-pressure space by the partition plate, and the low-pressure space includes a fixed scroll and a turning scroll. And an electric element for driving the orbiting scroll. The end plate is formed with a convex portion in which a part of the end surface is extended outward, and the fixed scroll includes a disk-shaped fixed scroll end plate and a fixed spiral wrap erected on the fixed scroll end plate. When the fixed wrap inner wall formed between 360 ° from the end of winding of the fixed spiral wrap is 360 °, the innermost wall outermost portion is turned. During driving, it provides a scroll compressor which is covered at all times by the end surface of the orbiting scroll end plate. According to the first aspect, since the contour line of the edge portion of the end plate of the orbiting scroll is always located outside the outermost periphery portion of the inner wall of the fixed scroll, the outermost periphery portion of the inner wall of the fixed scroll and the end plate edge portion of the orbiting scroll are separated. Without being hit, 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, a compression chamber A is formed by the outer wall of the swirl wrap and the inner wall of the fixed wrap, and the inner wall of the swirl wrap and the fixed swirl wrap. A compression chamber B is formed with the outer wall of the fixed wrap, and the inner wall of the fixed wrap is extended to the end of winding end of the outer wall of the swirl wrap. A scroll compressor is provided in which the compression volume of the compression chamber B immediately after the intake is closed is made different. According to the second aspect, since the suction confining volume can be increased without increasing the diameter of the compressor element, the scroll compressor can be reduced in size.

According to a third aspect of the present disclosure, in addition to the first or second aspect, the third aspect of the present disclosure is installed in parallel with the end surface of the orbiting scroll end plate, and prevents the orbiting scroll from rotating and allows the orbiting movement relative to the fixed scroll. A rotation prevention mechanism is provided, the rotation prevention mechanism having a pair of first keys and a pair of second keys, a first imaginary line connecting the pair of first keys, and a pair A second imaginary line connecting the second keys of the first and second keys is substantially orthogonal, the orbiting scroll end plate has a pair of first key grooves, and the fixed scroll has a pair of second key grooves. And the first key is slid in the first keyway, the second key is slid in the second keyway, and the fixed scroll with respect to the orbiting scroll A scroll compressor having the anti-rotation mechanism disposed on the opposite side . According to the third aspect, when the Oldham ring is used as the rotation preventing mechanism, the first key and the second key provided on the Oldham ring are both arranged on the same surface of the Oldham ring. Therefore, the number of times the Oldham ring is detached from the processing apparatus during the processing of the Oldham ring is reduced, and the processing accuracy can be improved and the processing cost can be reduced.

According to a fourth aspect of the present disclosure, in addition to the third aspect, a scroll compressor in which a virtual intersection of the first virtual line and the second virtual line is offset with respect to a midpoint of the second virtual line. provide. According to the fourth aspect, the extension angle of the spiral wrap of the orbiting scroll and the fixed scroll can be increased, the compression chamber can be increased in volume at a high compression ratio, and the scroll compressor can be reduced in size with high efficiency.

According to a fifth aspect of the present disclosure, in addition to the first to fourth aspects, the swirl spiral wrap and the fixed spiral wrap are arranged on the outer periphery of each end plate from a winding start end located substantially at the center of each end plate. Provided is a scroll compressor in which the thickness of each wrap is gradually reduced toward the end of winding. According to the 5th aspect, a compression element can be reduced in weight and it can be set as a high compression ratio, and high efficiency and size reduction by high volume can be implement | achieved.

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. A partition plate 11 that divides the inside of the sealed container 10 up and down is provided at an upper portion in the sealed container 10. Inside the sealed container 10, the space above the partition plate 11 is a high-pressure space 12, and the space below the partition plate 11 is a low-pressure space 13.

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

The compression element 14 includes a fixed scroll 19 and a turning scroll 20. The fixed swirl wrap 32 of the fixed scroll 19 and the swirl swirl wrap 39 of the orbiting scroll 20 are engaged with each other, and a plurality of compression spaces (compression chambers) 21 are formed between the fixed swirl wrap 32 and the swirl spiral wrap 39. .
The fixed scroll 19 includes a disk-shaped fixed scroll end plate 31, a spiral fixed swirl wrap 32 erected on the lower end surface of the fixed scroll end plate 31, and a peripheral wall erected so as to surround the fixed swirl wrap 32. 33 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. The fixed scroll end plate 31 includes a columnar protruding portion (boss portion) 36 protruding from the upper surface. The protrusion 36 has a discharge port 35. The protruding portion 36 is fitted into a holding hole 37 formed in the partition plate 11, and the upper surface of the protruding portion 36 faces the high-pressure space 12.
The orbiting scroll 20 includes a disc-like orbiting scroll end plate 38 and an orbiting spiral wrap 39 standing on the upper end surface of the orbiting scroll end plate 38, and a cylindrical shape at the approximate center of the lower end surface of the orbiting scroll end plate 38. The boss 40 is formed.

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 approximate center thereof. An eccentric shaft 23 a that is eccentric with respect to the rotation shaft 23 is formed at the upper end of the rotation shaft 23. The eccentric shaft 23 a is inserted into the boss 40 through the swing bush 43 and the swing bearing 49 so as to be capable of being driven to rotate.

Further, the fixed scroll 19 is fixed to the main bearing 22 through the bolt penetrating part 34 a using a plurality of bolts 24 at the flange 34 of the fixed scroll 19. On the other hand, the orbiting scroll 20 is supported by the fixed scroll 19 via the Oldham ring 25. 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 sealed container 10 and a rotor 27 disposed inside the stator 26. A 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 used to balance 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 suction port 45 for lubricating oil at the lower end of the rotating shaft 23, and a paddle 46 formed at the upper portion of the suction port 45. The oil passage 44 is formed along the axial direction of the rotary shaft 23. Further, the oil passage 44 is provided with an oil supply port 47 for supplying lubricating oil at positions corresponding to the

bearings

28, 41, 49.

When the rotating shaft 23 rotates, the lubricating oil accumulated in the oil reservoir 16 enters the oil passage 44 from the suction port 45 of the rotating shaft 23 and is pumped upward along the paddle 46 of the oil passage 44. The pumped-up lubricating oil lubricates the

bearings

28, 41, and 49 through the oil supply ports 47. Further, the lubricating oil pumped up to the boss housing portion 42 is guided to the outer peripheral portion of the main bearing 22 through a return pipe 48 formed in the main bearing 22. Then, the lubricating oil is discharged from the discharge port 48a formed in the outer peripheral portion, and is returned to the oil reservoir 16 again.

FIG. 2 (a) is a side view of the orbiting scroll 20 in the present embodiment, and FIG. 2 (b) is an XX cross-sectional view.

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 including the convex portion 38b and on which the orbiting spiral wrap 39 is formed is indicated by a thick solid line among the outer peripheral edges of the orbiting scroll end plate 38 of the orbiting scroll 20. In addition, a pair of first key grooves 51 are formed in a part of the orbiting scroll end plate 38.
The convex portion 38b extends a part of the end surface of the orbiting scroll end plate 38 outward.
The orbiting spiral wrap 39 stands in a spiral shape on the orbiting scroll end plate 38 from the winding start end portion 39a located substantially at the center of the orbiting scroll end plate 38 to the winding end end portion 39b located on the outer periphery of the orbiting scroll end plate 38. ing.
The swirling spiral wrap 39 has a thickness of 39t, the outer peripheral surface is a swirling wrap outer wall 39out, and the inner peripheral surface is a swirling wrap inner wall 39in.
The thickness 39t of the swirl spiral wrap 39 is gradually reduced from the winding start end portion 39a to the winding end end portion 39b.

FIG. 3 is a bottom view of the fixed scroll 19 in the present embodiment.
The fixed spiral wrap 32 is provided in a spiral shape on the fixed scroll end plate 31 from the winding start end portion 32c positioned substantially at the center of the fixed scroll end plate 31 to the winding end end portion 32b positioned on the outer periphery of the fixed scroll end plate 31. ing.
The fixed spiral wrap 32 has a thickness 32t, the outer peripheral surface is a fixed wrap outer wall 32out, and the inner peripheral surface is a fixed wrap inner wall 32in.
The thickness 32t of the fixed spiral wrap 32 is gradually reduced from the winding start end portion 32c to the winding end end portion 32b.
In FIG. 3, the fixed wrap inner wall 32in formed between the end of the winding end 32b and 360 ° of the fixed wrap inner wall 32in of the fixed spiral wrap 32 is defined as an inner wall outermost peripheral portion 32a. The part 32a is indicated by a thick broken line.

A suction portion 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 pair of second key grooves 50 are formed in a part of the flange 34. ing.

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 compression chambers A and B of the scroll compressor 100 in the present embodiment.

FIG. 4A shows a state in which the compression chamber A formed by the swirling wrap outer wall 39out of the swirling spiral wrap 39 and the fixed wrap inner wall 32in of the fixed swirl wrap 32 has been completely closed by suction.

FIG. 4 (b) shows a state in which 90 ° rotation has advanced from FIG. 4 (a).

FIG. 4C shows a state in which the compression chamber B formed by the swirling wrap inner wall 39in of the swirling swirl wrap 39 and the fixed wrap outer wall 32out of the fixed swirl wrap 32 is immediately after the suction is closed (FIG. 4C). The state where the rotation of 180 ° is advanced from the state of 4 (a)).

FIG. 4 (d) shows a state where the rotation has further advanced by 90 ° from FIG. 4 (c).

Of the positions of the orbiting scroll 20 and the fixed scroll 19 at each rotation angle described above, the position where the orbiting scroll 20 is farthest from the suction portion 29 (around 180 °) is the edge portion 38a of the orbiting scroll 20 and the inner wall of the fixed scroll 19. The outermost peripheral part 32a is closest. However, according to the scroll compressor 100 in the present embodiment, by providing the convex portion 38b so as to widen the outer diameter part of the orbiting scroll end plate 38 of the orbiting scroll 20 to the outside, while the orbiting scroll 20 is orbitally driven, The edge portion 38 a of the orbiting scroll 20 always covers the inner wall outermost peripheral portion 32 a of the fixed scroll 19. That is, the edge portion 38 a of the orbiting scroll end plate 38 is always outside the innermost outermost peripheral portion 32 a of the fixed scroll 19. Therefore, even when the orbiting scroll 20 bends or falls during the operation of the scroll compressor 100, 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 are always stable. The driven state can be maintained, and high reliability can be realized.

By the way, the expansion angle of the winding end end portion 32b of the fixed wrap inner wall 32in of the fixed scroll 19 is reduced except that the convex portion 38b is provided so that the outer diameter part of the orbiting scroll end plate 38 of the orbiting scroll 20 is expanded outward. Even if the fixed wrap inner wall 32in is terminated at a position closer to the central portion of the fixed scroll end plate 31 with respect to the radial direction of the fixed scroll 19, the edge portion 38a of the orbiting scroll 20 remains in the orbiting driving of the compression element 14. The inner wall outermost peripheral portion 32a of the fixed scroll 19 can always be covered. However, in this method, the confining volume of the compression chamber A is reduced, so that the heights of the fixed spiral wrap 32 and the swirl spiral wrap 39 need to be designed to be large in order to achieve an equivalent volume. However, by raising the fixed spiral wrap 32 and the swirl spiral wrap 39, the reliability of the spiral wraps 32, 39 is lowered, the rollover strength is lowered, and the workability is lowered. In addition, since the compression ratio of the compression chamber A is also reduced, insufficient compression is likely to occur, and the efficiency of the scroll compressor 100 is reduced.

Also, by increasing the outer diameter of the orbiting scroll end plate 38, the edge portion 38 a of the orbiting scroll 20 can always cover the outermost peripheral portion 32 a of the inner wall of the fixed scroll 19 during the orbiting drive of the compression element 14. However, the maximum outer diameter of the orbiting scroll end plate 38 can be designed only within a range in which the orbiting scroll end plate 38 does not contact the bolt penetrating portion 34a that forms the fastening portion between the fixed scroll 19 and the main bearing 22. In order to increase the outer diameter of the orbiting scroll end plate 38, it is necessary to reduce the bolt penetrating portion 34a and use a bolt having a thinner nominal diameter. For this reason, problems such as poor mechanical fixing due to a decrease in rigidity of the fixing portion between the fixed scroll 19 and the main bearing 22 and a decrease in bolt tightening force occur.

For this reason, both the high reliability and the 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 the present embodiment form the fixed wrap inner wall 32in of the fixed spiral wrap 32 up to the vicinity of the outer wall winding end portion 39b of the orbital spiral wrap 39, and the compression element 14 is engaged. The two confined volumes of the compression chamber A and the compression chamber B are made different.

Such a configuration is desirable from the viewpoint of downsizing the scroll compressor 100 because the suction confining volume can be increased without increasing the diameter of the compression element 14.

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 pair of first keys 53 and a pair of second keys 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. The first key 53 slides in the first keyway 51, and the second key 52 slides in the second keyway 50. 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 above in the direction of the rotation axis 23.

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 on the same surface 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. Improvement in accuracy and reduction in machining costs can be obtained.

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. The distance to 39 can be increased. As a result, since the outermost peripheral distance of the orbiting spiral wrap 39 can be increased from the center of the orbiting scroll end plate 38, the extension angle of the orbiting 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 100 can be made more efficient and smaller.

Further, as shown in FIG. 4, the convex portion 38b is provided at a position overlapping with the suction portion 29 in the axial direction, so that the necessary convex portion 38b area can be minimized, thereby obtaining an effect of further weight reduction. be able to.

The inner and outer wall curves of the fixed spiral wrap 32 and the swirl spiral wrap 39 are expressed by the following equations, for example, where a is a basic circle radius, θ is an extension angle, ε is a swirl radius, and B and n are coefficients. And the coefficient B satisfies B> 0.
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 θ- (a · (θ−π) −B · (θ−π) n + ε) · cos θ (4) (inner wall Y coordinate)

According to such a configuration, the

thicknesses

32t and 39t of the winding

end portions

32b and 39b of the spiral wraps 32 and 39 can be reduced, so that the compression element 14 can be reduced in weight. In particular, the orbiting scroll 20 can reduce the load on the bearing portion 41 and the orbiting bearing 49 due to the effect of reducing the centrifugal force at the time of orbiting driving due to the weight reduction, and the balance weight 55 provided on the rotary 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.

In the above-described configuration, the

thicknesses

32t and 39t of the spiral wraps 32 and 39 decrease toward the winding

end portions

32b and 39b of the spiral wraps 32 and 39, so that the rigidity of the spiral wraps 32 and 39 is reduced. However, when combined with the configuration in which the convex portion 38b is formed on the orbiting scroll 20 as in the present embodiment, it is possible to prevent the end contact between the end plate edge portion 38a of the orbiting scroll 20 and the outermost peripheral portion 32a of the inner wall of the fixed scroll 19. . Therefore, the reliability of the spiral wraps 32 and 39 is not reduced due to abnormal vibration or the like caused by one piece, and 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 with bolts 24. However, even if the fixed scroll 19 can be moved only in the direction of the rotary shaft 23 and pressed downward by the high pressure of the high-pressure space 12, the convex portion 38b of the orbiting scroll 20 of this embodiment can be formed similarly. It goes without saying that the effects of can be obtained.

The present invention is useful for a compressor of a refrigeration cycle apparatus that can be used for electrical products such as a water heater, a hot water heater, and an air conditioner.

DESCRIPTION OF SYMBOLS 10 Airtight container 11 Partition plate 12 High pressure space 13 Low pressure 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 Fixed spiral wrap 39 Orbital spiral wrap 33 Perimeter wall 34 Flange 35 Discharge port 38 Orbiting scroll end plate

Claims

A partition plate is provided in the sealed container,
By the partition plate, the inside of the sealed container is divided into a low pressure space and a high pressure space,
In the low-pressure space, a compression element having a fixed scroll and a turning scroll, and an electric element that drives the turning scroll to turn,
The orbiting scroll includes a disc-shaped orbiting scroll end plate and an orbiting spiral wrap erected on an end surface of the orbiting scroll end plate, and the orbiting scroll end plate has a part of the end surface extended outward. Forming convex parts,
The fixed scroll includes a disk-shaped fixed scroll end plate, and a fixed spiral wrap erected on the fixed scroll end plate,
When the fixed wrap inner wall formed between the end of winding of the fixed spiral wrap and 360 ° is the innermost wall outer periphery,
The scroll compressor according to claim 1, wherein the outermost peripheral portion of the inner wall is always covered with the end face of the orbiting scroll end plate during the orbiting drive.
A compression chamber A is formed by the swirl wrap outer wall of the swirl spiral wrap and the fixed wrap inner wall,
A compression chamber B is formed by the inner wall of the swirl wrap and the outer wall of the fixed swirl wrap,
By extending the inner wall of the fixed wrap to the end of winding of the outer wall of the orbiting wrap, the closed volume of the compression chamber A when the suction confinement is completed, and the compression chamber B immediately after the intake confinement is closed. The scroll compressor according to claim 1, wherein the confining volume is different.
A rotation prevention mechanism that is installed in parallel with the end face of the orbiting scroll end plate, prevents rotation of the orbiting scroll and allows orbiting movement with respect to the fixed scroll;
The rotation prevention mechanism has a pair of first keys and a pair of second keys,
A first imaginary line connecting the pair of first keys and a second imaginary line connecting the pair of second keys are substantially orthogonal;
The orbiting scroll end plate has a pair of first key grooves,
The fixed scroll has a pair of second key grooves,
Sliding the first key in the first keyway, sliding the second key in the second keyway,
The scroll compressor according to claim 1, wherein the rotation prevention mechanism is disposed on the opposite side of the fixed scroll with respect to the orbiting scroll.
The scroll compressor according to claim 3, wherein a virtual intersection of the first virtual line and the second virtual line is offset with respect to a midpoint of the second virtual line.
The swirl spiral wrap and the fixed spiral wrap are formed by gradually reducing the thickness of each wrap from the winding start end located substantially at the center of each end plate to the winding end end located on the outer periphery of each end plate. The scroll compressor according to any one of claims 1 to 4, wherein the scroll compressor is provided.