JP2010196663A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of properly releasing heat generated in the compressor, reducing its size and increasing its capacity. <P>SOLUTION: In a turning scroll 20X and fixed scroll 30X, lap walls 22A, 22B, 32A, 32B are arranged on both surface of an end plate 21 and compression spaces 50A, 50B are formed on both surface sides of the end plate 21. A boss 18 of a main shaft 12 is inserted to a recessed part 23 formed at a main shaft 12 side of the end plate 21 of the turning scroll 20X via a drive bush 24, lubrication between the recessed part 23 and the drive bush 24 is performed by a lubricating oil contained in a refrigerant and heat accumulated in a center part of the turning scroll 20X is released to outside via this lubricating oil. The lap heights of the turning scroll 20X and the fixed scroll 30X are gradually lowered from an outer circumferential side to an inner circumferential side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a scroll type compressor used for an air conditioner or the like.

  A scroll type compressor used for an air conditioner or the like includes a fixed scroll and a turning scroll. Each of the fixed scroll and the orbiting scroll is formed by integrally forming a spiral wrap wall on one surface side of a disk-shaped end plate. The fixed scroll and the orbiting scroll are made to face each other with the wrap wall meshed, and the orbiting scroll revolves with respect to the fixed scroll, and the compression space formed between the two wrap walls is made from the outer peripheral side. The fluid in the compression space is compressed by reducing the volume while moving to the inner peripheral side.

In compressors, scroll-type compressors are always required to be smaller and have a larger capacity. When trying to reduce the size and capacity of the compressor, it is conceivable to raise the wrap walls of the fixed scroll and the orbiting scroll.
However, when the wrap wall is excessively high, there arises a problem that strength reliability of the wrap wall is lowered. On the other hand, increasing the rigidity of the wrap wall leads to an increase in size and weight of the compressor, which is not preferable.

  Accordingly, wrap walls are formed on both surfaces of the end plate of the orbiting scroll, and two sets of wrap walls are provided on the fixed scroll side so as to face each of the wrap walls on both sides of the end plate of the orbiting scroll. The compression space volume is increased while suppressing the height (see, for example, Patent Document 1).

JP 59-15690 A

In the scroll compressor, as described above, the orbiting scroll is revolved with respect to the fixed scroll so that the compression space formed between the fixed scroll and the orbiting scroll is directed from the outer peripheral side to the inner peripheral side. The volume is reduced while turning. At this time, the volume of the compression space decreases, and the refrigerant temperature rises as the pressure of the refrigerant in the compression space increases. As a result, due to the heat of the refrigerant, the temperatures of the fixed scroll and the orbiting scroll become higher at the center.
In particular, as in the technique described in Patent Document 1, when wrap walls are provided on both sides of the end plate of the orbiting scroll, the heat accumulated in the center of the fixed scroll and orbiting scroll is less likely to be released. In view of durability, reliability and the like, it is not preferable.

  Furthermore, there is a constant demand for further downsizing and larger capacity of the compressor, and there is a need for improvement in this respect as well.

  The present invention has been made based on such a technical problem, and can efficiently release heat generated in the compressor, and can achieve further downsizing and larger capacity. The purpose is to provide.

For this purpose, the present invention is a scroll-type compressor, which is rotatably connected to a main shaft rotatably supported in a housing forming an outer shell, and a position offset with respect to the center of the main shaft. And a fixed scroll that is fixed to the housing and forms a compression space that compresses the refrigerant by facing the orbiting scroll. The orbiting scroll has spiral-shaped orbiting scroll side wrap walls formed on both sides of the disk-shaped end plate, and the fixed scroll faces the orbiting scroll side wrap walls formed on both sides of the end plate of the orbiting scroll. A pair of fixed scroll side wrap walls are formed. And a recessed part is formed in the center part of the one surface side of the end plate of the orbiting scroll, and an eccentric boss provided eccentrically from the central axis of the main shaft at the tip part of the main shaft is inserted into the recessed part via a bearing. It is characterized by.
As described above, the orbiting scroll side wrap walls are formed on both surfaces of the end plates of the orbiting scroll, and the fixed scroll side wrap walls facing the respective orbiting scroll side wrap walls are formed. Is compressed.
In such a configuration, the gap between the concave portion formed in the center portion on the one surface side of the end plate of the orbiting scroll and the eccentric boss provided eccentric from the center of the main shaft is lubricated with lubricating oil. With this lubricating oil, heat at the center of the fixed scroll and the orbiting scroll can be released.

The compression space formed between the orbiting scroll and the fixed scroll gradually decreases in cross-sectional area from the outer peripheral side toward the inner peripheral side. In the present invention, however, the orbiting scroll side wrap wall and the fixed scroll side are further reduced. The lap height with the wrap wall gradually decreases from the outer peripheral side toward the inner peripheral side.
Thereby, the compression ratio of the compressor can be further increased.

By the way, since the concave part for inserting the eccentric boss is formed in the central part on the one surface side of the end plate of the orbiting scroll, the area of the compression chamber on the one surface side of the end plate of the orbiting scroll is the same as that of the orbiting scroll. It becomes smaller than the other surface side of the end plate, and the pressure balance is lost between the one surface side and the other surface side of the end plate of the orbiting scroll. Therefore, in the orbiting scroll and the fixed scroll, the orbiting scroll side wrap wall formed on one side of the end plate and the wrap height of the fixed scroll side wrap wall, and the orbiting scroll side wrap wall formed on the other side of the end plate. The wrap heights of the fixed scroll side wrap walls are preferably different from each other.
As a result, it is possible to achieve a pressure balance between the one surface side and the other surface side of the end plate of the orbiting scroll.

  In the orbiting scroll and the fixed scroll, the orbiting scroll side wrap wall and the fixed scroll side wrap wall formed on one side of the end plate, and the orbiting scroll side wrap wall and the fixed scroll side wrap formed on the other side of the end plate The wall may be spirally wound in different directions. Thereby, the direction of the compressive force which arises in the compression space of a refrigerant | coolant by the one side and the other side of an end plate can be made into the direction which opposes on both sides of the axis line of a main axis | shaft.

Further, the present invention is a scroll type compressor, which is a main shaft rotatably supported in a housing forming an outer shell, and a turning scroll rotatably connected to a position offset with respect to the center of the main shaft. And a fixed scroll that is fixed to the housing and forms a compression space that compresses the refrigerant by facing the orbiting scroll, and the orbiting scroll has spiral-shaped orbiting scroll sides on both sides of the disk-shaped end plate, respectively. A wrap wall is formed, and the fixed scroll is formed with a pair of fixed scroll side wrap walls facing each of the orbiting scroll side wrap walls formed on both sides of the end plate of the orbiting scroll, and between the orbiting scroll and the fixed scroll. The cross-sectional area of the compression space formed at the outer peripheral side gradually decreases from the outer peripheral side toward the inner peripheral side. Wrap height of the Le side wrap wall, it may be characterized by gradually reducing toward the outer side.
Further, in the orbiting scroll and the fixed scroll, the orbiting scroll side wrap wall and the fixed scroll side wrap wall formed on one side of the end plate, and the orbiting scroll side wrap wall and the fixed scroll formed on the other side of the end plate. The side wrap walls may be spirally wound in different directions.

  According to the present invention, the orbiting scroll side wrap walls are formed on both surfaces of the end plate of the orbiting scroll, and the fixed scroll side wrap walls facing the respective orbiting scroll side wrap walls are formed on both sides of the end plate. Each refrigerant is compressed, and the compression capacity of the compressor can be increased. In such a configuration, the orbiting scroll is lubricated between the recess formed in the center portion on the one surface side of the end plate of the orbiting scroll and the eccentric boss provided eccentric from the center of the main shaft. The heat generated in the center of the compressor can be released, and the heat generated inside the compressor can be released well.

  In addition, the compression ratio of the compressor can be further increased by further reducing the height of the orbiting scroll side wrap wall and the fixed scroll side wrap wall from the outer peripheral side toward the inner peripheral side. And large capacity can be realized.

It is sectional drawing of the scroll type compressor in 1st embodiment. It is sectional drawing which shows the fixed scroll and turning scroll of the compressor of FIG. It is sectional drawing which shows the fixed scroll of the compressor in 2nd embodiment, and a turning scroll. It is sectional drawing which shows the fixed scroll of the compressor in 3rd embodiment, and a turning scroll. In the compressor of FIG. 4, it is a figure which shows the fixed scroll and turning scroll which form the compression space of one side of the end plate of a turning scroll, and the fixed scroll and turning scroll which form the compression space of the other side, (a) is a figure which shows the state whose turning angle of a turning scroll is 360 degrees, (b) is a turning angle of 270 degrees. In the compressor of FIG. 4, it is a figure which shows the fixed scroll and turning scroll which form the compression space of one side of the end plate of a turning scroll, and the fixed scroll and turning scroll which form the compression space of the other side, (c) is a figure which shows the state in which the turning angle of a turning scroll is 180 degrees, (d) is a state in which a turning angle is 90 degrees.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
[First embodiment]
FIG. 1 is a cross-sectional view for explaining the configuration of the compressor in the present embodiment.
As shown in FIG. 1, the compressor 10X is a vertical scroll type, and includes a main shaft 12, a turning scroll 20X that rotates together with the main shaft 12, a fixed scroll 30X fixed to the housing 11, and a housing 11. Is provided.
In such a compressor 10X, the refrigerant is introduced into the housing 11 from the refrigerant introduction port P1 formed on one end side of the housing 11, and the refrigerant is compressed in the compression space formed between the orbiting scroll 20X and the fixed scroll 30X. Is compressed. The compressed refrigerant is discharged from a refrigerant discharge port P <b> 2 formed on the other end side of the housing 11.

As shown in FIG. 2, the orbiting scroll 20 </ b> X has spiral wrap walls (orbiting scroll side wrap walls) 22 </ b> A and 22 </ b> B integrally formed on both sides of the disc-shaped end plate 21. Is formed.
On the other hand, the fixed scroll 30X has a pair of end plates 31A and 31B that are opposed to each other with the orbiting scroll 20X interposed therebetween, and the end plates 31A and 31B are spirals that engage with the wrap walls 22A and 22B of the orbiting scroll 20X, respectively. Shaped wrap walls (fixed scroll side wrap walls) 32A, 32B are formed. Here, the fixed scroll 30X includes the upper fixed scroll member 33A including the end plate 31A and the wrap wall 32A located on one side of the orbiting scroll 20X, and the end plate 31B and wrap wall located on the other side. And a lower fixed scroll member 33B made of 32B. As shown in FIG. 1, the upper fixed scroll member 33A and the lower fixed scroll member 33B are integrally fastened by a plurality of bolts 34 on the outer peripheral side of the orbiting scroll 20X.

In this way, the orbiting scroll 20X and the fixed scroll 30X are configured such that the wrap wall 22A and the wrap wall 32A are combined with each other on one side of the end plate 21 of the orbiting scroll 20X, and the wrap wall 22B on the other side of the end plate 21. The wrap walls 32B are combined with each other. Thereby, the orbiting scroll 20X and the fixed scroll 30X form compression spaces 50A and 50B, respectively, on both sides of the orbiting scroll 20X.
The compression space 50 </ b> A formed on the main shaft 12 side of the orbiting scroll 20 </ b> X and the compression space 50 </ b> B formed on the other surface side communicate with each other via a communication hole 25 formed in the end plate 21.
Thereby, the refrigerant introduced into the upper and lower compression spaces 50A and 50B from the suction hole 51 in the outer peripheral portion is sequentially sent from the outer peripheral side to the inner peripheral side and compressed by the revolution of the orbiting scroll 20X with respect to the fixed scroll 30X. The refrigerant compressed in the compression space 50A merges with the refrigerant compressed in the compression space 50B on the other surface side through the communication hole 25. As shown in FIG. 1, the merged refrigerant covers the fixed scroll 30X above the fixed scroll 30X, the discharge hole 37 formed in the upper part of the fixed scroll 30X, the reed valve 38 provided in the discharge hole 37, and the fixed scroll 30X. The refrigerant is discharged from a refrigerant discharge port P2 formed on the other end side of the housing 11 through a reed valve 40 provided on the upper cover 39 provided.

  Both ends of the main shaft 12 are rotatably supported by the housing 11 via bearings 13 and 14. The main shaft 12 is rotationally driven by a motor 17 including a stator 15 fixed to the inner surface of the housing 11 and a rotor 16 fixed to the outer peripheral surface of the main shaft 12 and facing the stator 15. The main shaft 12 is driven to rotate by one end of the main shaft 12 projecting outside through the housing 11 and connected to one end of the main shaft 12 by a driving source (not shown) such as an engine or a motor provided outside. You can also

As shown in FIG. 2, a boss 18 protrudes from the other end of the main shaft 12 at a position eccentric from the central axis of the main shaft 12 by a predetermined dimension. A recess 23 for accommodating the boss 18 is formed on the main shaft 12 side of the orbiting scroll 20X. The boss 18 is inserted into the recess 23 via a drive bush (bearing) 24, whereby the orbiting scroll 20X is rotatably held by the boss 18. Accordingly, the orbiting scroll 20X is provided eccentrically by a predetermined dimension with respect to the center of the main shaft 12, and when the main shaft 12 rotates around its axis, the orbiting scroll 20X is eccentric with respect to the center of the main shaft 12. Performs rotation (revolution) with the dimensions as the radius. An Oldham ring 19 is interposed between the orbiting scroll 20X and the main shaft 12 so that the orbiting scroll 20X does not rotate while revolving.
Further, the main shaft 12 is formed with a lubricating oil passage 12 a for supplying the lubricating oil sucked up from the oil reservoir at the bottom of the housing 11 from the upper end portion of the main shaft 12 to the drive bush 24 between the main shaft 12 and the recess 23. Has been.

  Now, in order to increase the degree to which the cross-sectional areas of the compression spaces 50A and 50B formed between the orbiting scroll 20X and the fixed scroll 30X gradually decrease from the outer peripheral side toward the inner peripheral side, On both sides of the end plate 21, the wrap height of the orbiting scroll 20X and the fixed scroll 30X is gradually reduced from the outer peripheral side toward the inner peripheral side. For this purpose, the wrap walls 22A and 22B of the orbiting scroll 20X and the wrap walls 32A and 32B of the fixed scroll 30X are formed so as to be gradually reduced from the outer peripheral side to the inner peripheral side. The height of the wrap walls 22A, 22B, 32A, 32B may be gradually increased from the outer peripheral side to the inner peripheral side of the fixed scroll 30X (stepwise), or continuously increased and spiraled. You may form in a shape.

In the example of FIG. 2, with respect to the virtual center line C in the thickness direction of the end plate 21 of the orbiting scroll 20 </ b> X, the dimension to the tip of the wrap walls 22 </ b> A and 22 </ b> B The dimension H2 is formed so as to gradually become smaller. Further, the end plate 21 of the orbiting scroll is formed such that the inner peripheral thicknesses T4 and T5 are larger than the outer peripheral thickness T3 with respect to the virtual center line C in the thickness direction.
On the other hand, the end plates 31A and 31B of the fixed scroll 30X have an inner peripheral portion thickness T2 larger than the outer peripheral portion thickness T1 so as to face the tip portions of the wrap walls 22A and 22B with a predetermined minute clearance. Is formed. Accordingly, the height to the tip of the wrap walls 32A and 32B of the fixed scroll 30X corresponds to the wrap walls 22A and 22B of the orbiting scroll 20X, and the inner dimension H2 relative to the outermost dimension H1. Is formed to be small.
In this way, on both sides of the end plate 21 of the orbiting scroll 20X, the wrap heights L1 and L2 of the orbiting scroll 20X and the fixed scroll 30X are gradually reduced from the outer peripheral side toward the inner peripheral side.

  In the example of FIG. 2, in the orbiting scroll 20X and the fixed scroll 30X, the wrap height of the wrap walls 22A and 32A formed on one side of the end plate 21 of the orbiting scroll 20X and the other side of the end plate 21 The wrap heights of the formed wrap walls 22B and 32B are different from each other. Specifically, the wrap height of the wrap walls 22A and 32A on the side of the main shaft 12 where the recess 23 for accommodating the boss 18 is formed is higher than the wrap height of the wrap walls 22B and 32B on the other side. Is set.

  According to the configuration as described above, the recess 23 that accommodates the boss 18 is formed on the main shaft 12 side of the orbiting scroll 20 </ b> X, and the boss 18 is inserted into the recess 23 via the drive bush 24. Such a recess 23 and the drive bush 24 are lubricated by the lubricating oil contained in the refrigerant. Thereby, the heat accumulated in the central portion of the orbiting scroll 20X can be released to the outside through this lubricating oil, and durability and reliability can be improved.

Moreover, the compressor 10X is formed between the orbiting scroll 20X and the fixed scroll 30X because the wrap height of the orbiting scroll 20X and the fixed scroll 30X is gradually reduced from the outer peripheral side toward the inner peripheral side. The cross section of the compression space is reduced not only in the radial direction but also in the height direction. As a result, the compression ratio of the compressor 10X can be increased. Further, in the orbiting scroll 20X and the fixed scroll 30X, by increasing the height of the outer peripheral wrap walls 22A, 22B, 32A and 32B, the capacity of the orbiting scroll 20X and the fixed scroll 30X can be increased without increasing the outer diameter. Increase is possible. As a result, the compressor 10X can be further reduced in size and capacity.
Moreover, in the orbiting scroll 20X and the fixed scroll 30X, the height of the central wrap walls 22A, 22B, 32A, and 32B, where the load load due to compression is large, can be suppressed, so the strength of the orbiting scroll 20X and the fixed scroll 30X is improved. And high reliability can be obtained.
Further, by forming compression spaces on both sides of the end plate 21 of the orbiting scroll 20X, it is possible to balance the compression load in the axial direction (thrust direction) of the main shaft 12 of the compressor 10X, and to reduce the loss due to the thrust load. Can be suppressed.

  In addition, the wrap height of the wrap walls 22A and 32A formed on one side of the end plate 21 of the orbiting scroll 20X and the wrap height of the wrap walls 22B and 32B formed on the other side of the end plate 21 are: I tried to make them different from each other. Thereby, even if the cross-sectional area of the compression space is different between the one side and the other side of the end plate 21 of the orbiting scroll 20X by forming the recess 23, the pressure balance is maintained on both sides of the end plate 21 of the orbiting scroll 20X. It becomes possible to take.

[Second Embodiment]
Next, a second embodiment of the compressor according to the present invention will be described.
In the following, only points different from the configuration shown in the first embodiment will be described, and components common to the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
Here, the orbiting scroll 20X of the compressor 10X shown in the first embodiment has been rotationally driven by inserting the boss 18 of the main shaft 12 into the center of the orbiting scroll 20X. As shown, the compressor 10Y described below is different in that the orbiting scroll 20Y is rotationally driven by two crankshafts as in the technique described in Japanese Patent Application Laid-Open No. 59-15690, for example.

That is, as shown in FIG. 3, the compressor 10 </ b> Y includes the orbiting scroll 20 </ b> Y provided to be rotatable in the housing 11 as in FIG. 1, and the fixed scroll 30 </ b> Y fixed to the housing 11.
In the orbiting scroll 20Y, wrap walls (orbiting scroll side wrap walls) 22C and 22D each having a predetermined height are integrally formed on both sides of the disc-shaped end plate 21.
On the other hand, the fixed scroll 30Y has a pair of end plates 31C and 31D that are opposed to each other with the orbiting scroll 20Y in between, and the end plates 31C and 31D are spirals that mesh with the wrap walls 22C and 22D of the orbiting scroll 20Y. Shaped wrap walls (fixed scroll side wrap walls) 32C and 32D are formed.

Here, the orbiting scroll 20Y is fixed to the fixed scroll 30Y by a pair of crankshafts 61 and 61 arranged on the outer periphery of the orbiting scroll 20Y, as in the configuration described in FIG. 7 of Japanese Patent Laid-Open No. 59-15690. Rotation (revolution) is performed with a radius that is eccentric by a predetermined dimension. That is, the pair of crankshafts 61 and 61 each have a driven gear 62 and mesh with a drive gear 63 provided on the main shaft 12. When the main shaft 12 is rotated by a motor or the like, the crankshafts 61 and 61 are rotationally driven. Is done. Each crankshaft 61 is provided with an eccentric boss 64 that is eccentric with respect to the center thereof. The eccentric boss 64 is inserted into a recess 65 formed in the end plate 21 of the orbiting scroll 20Y via a bearing (not shown). Has been inserted.
Thereby, when the crankshaft 61 rotates, the orbiting scroll 20Y revolves around the center of the fixed scroll 30Y as the eccentric boss 64 turns.

The orbiting scroll 20Y and the fixed scroll 30Y are configured such that the wrap wall 22C and the wrap wall 32C are combined with each other on one side of the end plate 21 of the orbiting scroll 20Y, and the wrap wall 22D and wrap wall 32D are connected to each other on the other side of the end plate 21. Combined. Thus, the orbiting scroll 20Y and the fixed scroll 30Y form compression spaces 50C and 50D on both sides of the orbiting scroll 20Y, respectively.
A compression space 50 </ b> C formed on the main shaft 12 side of the orbiting scroll 20 </ b> Y and a compression space 50 </ b> D formed on the other surface side communicate with each other through a communication hole 26 formed in the end plate 21.
Thereby, the refrigerant introduced into the upper and lower compression spaces 50C, 50D from the suction hole 51 in the outer peripheral portion is sequentially sent from the outer peripheral side to the inner peripheral side and compressed by the revolution of the orbiting scroll 20Y with respect to the fixed scroll 30Y. The refrigerant compressed in the compression space 50C merges with the refrigerant compressed in the compression space 50D on the other surface side through the communication hole 26. The merged refrigerant passes through the discharge hole 37 formed in the upper part of the fixed scroll 30Y, the reed valve 38 provided in the discharge hole 37, and the reed valve 40 provided in the upper cover 39 as shown in FIG. Then, the refrigerant is discharged from the refrigerant discharge port P2 formed on the other end side of the housing 11.

Now, in order to increase the degree to which the cross-sectional areas of the compression spaces 50C and 50D formed between the orbiting scroll 20Y and the fixed scroll 30Y gradually decrease from the outer peripheral side toward the inner peripheral side, FIG. In the same manner as described above, the wrap heights L1 and L2 of the orbiting scroll 20Y and the fixed scroll 30Y are gradually reduced from the outer peripheral side toward the inner peripheral side on both sides of the end plate 21 of the orbiting scroll 20Y. For this, the wrap walls 22C and 22D of the orbiting scroll 20Y and the wrap walls 32C and 32D of the fixed scroll 30Y are formed so as to be gradually reduced from the outer peripheral side to the inner peripheral side. The height of the wrap walls 22C, 22D, 32C, 32D may be gradually increased from the outer peripheral side to the inner peripheral side of the fixed scroll 30Y (stepwise), or continuously increased to be spiral. You may form in a shape.
Here, the wrap walls 22C and 22D and 32C and 32D have the same shape and the same phase above and below the end plate 21.

According to the configuration as described above, the compressor 10Y is configured such that the wrap height of the orbiting scroll 20Y and the fixed scroll 30Y is gradually reduced from the outer peripheral side toward the inner peripheral side. The cross section of the compression space formed between the two is reduced not only in the radial direction but also in the height direction. As a result, the compression ratio of the compressor 10Y can be increased. Further, in the orbiting scroll 20Y and the fixed scroll 30Y, by increasing the height of the outer peripheral wrap walls 22C, 22D, 32C and 32D, the capacity of the orbiting scroll 20Y and the fixed scroll 30Y can be increased without increasing the outer diameter. Increase is possible. Thereby, further size reduction and capacity increase of the compressor 10Y can be achieved.
Moreover, in the orbiting scroll 20Y and the fixed scroll 30Y, the height of the central wrap walls 22C, 22D, 32C, and 32D, where the load load due to compression is large, can be suppressed, so the strength of the orbiting scroll 20Y and the fixed scroll 30Y is improved. And high reliability can be obtained.
Further, by forming the compression spaces 50C and 50D on both sides of the end plate 21 of the orbiting scroll 20Y, it is possible to balance the compression load in the axial direction (thrust direction) of the main shaft 12 of the compressor 10Y. The loss due to can be suppressed.

[Third embodiment]
Next, a third embodiment according to the present invention will be described.
In the following, only points different from the configuration shown in the second embodiment will be described, and the components common to the second embodiment will be denoted by the same reference numerals and description thereof will be omitted.
Here, the compressor 10Z shown in the present embodiment is different from the compressor 10Y shown in the second embodiment in the wrap walls (orbiting scroll side wrap walls) 22E and 22F of the orbiting scroll 20Z and the fixed scroll 30Z. The only difference is that the wrap walls (fixed scroll side wrap walls) 32E and 32F are spirally formed in different directions on one side and the other side of the end plates 21 and 31, respectively.

That is, as shown in FIG. 4, the compressor 10 </ b> Z includes a orbiting scroll 20 </ b> Z provided so as to be rotatable in the housing 11, and a fixed scroll 30 </ b> Z fixed to the housing 11.
The orbiting scroll 20Z is integrally formed with wrap walls 22E and 22F that are spiral and have a predetermined height on both sides of the disc-shaped end plate 21.
On the other hand, the fixed scroll 30Z has a pair of end plates 31E and 31F that are opposed to each other with the orbiting scroll 20Z interposed therebetween, and the end plates 31E and 31F are spirals that engage with the wrap walls 22E and 22F of the orbiting scroll 20Z, respectively. Shaped wrap walls 32E and 32F are formed.

  Here, as shown in FIGS. 5 and 6, in the orbiting scroll 20 </ b> Z, the wrap wall 22 </ b> E provided on one side of the end plate 21 and the wrap wall 22 </ b> F provided on the other side are spirally wound. The directions are different from each other, and the phases are line-symmetric. Also, in the fixed scroll 30Z, the one wrap wall 32E and the other 32F are different from each other in the spiral winding direction, and their phases are axisymmetric.

In such a compressor 10Z, the orbiting scroll 20Z and the fixed scroll 30Z are combined with each other on one side of the end plate 21 of the orbiting scroll 20Z with the wrap wall 22E and the wrap wall 32E, and on the other side of the end plate 21. The wrap wall 22F and the wrap wall 32F are combined with each other. Thus, the orbiting scroll 20Z and the fixed scroll 30Z form compression spaces 50E and 50F on both sides of the orbiting scroll 20Z, respectively.
The refrigerant introduced into the upper and lower compression spaces 50E and 50F from the suction hole 51 in the outer peripheral portion is sequentially sent from the outer peripheral side to the inner peripheral side and compressed by the revolution of the orbiting scroll 20Z with respect to the fixed scroll 30Z. The refrigerant compressed in the compression space 50E merges with the refrigerant compressed in the compression space 50F on the other surface side through the communication hole 26. The merged refrigerant passes through a discharge hole 37 formed in the upper part of the fixed scroll 30Z, and further through a reed valve 38 provided in the discharge hole 37 and a reed valve 40 provided in the upper cover 39 as shown in FIG. The refrigerant is discharged from the refrigerant discharge port P2 formed on the other end side of the housing 11.

  Now, in order to increase the degree to which the cross-sectional areas of the compression spaces 50E and 50F formed between the orbiting scroll 20Z and the fixed scroll 30Z gradually decrease from the outer peripheral side toward the inner peripheral side, On both sides of the end plate 21, the wrap heights L1 and L2 of the orbiting scroll 20Z and the fixed scroll 30Z are gradually reduced from the outer peripheral side toward the inner peripheral side. For this, the wrap walls 22E and 22F of the orbiting scroll 20Z and the wrap walls 32E and 32F of the fixed scroll 30Z are formed so as to be gradually reduced from the outer peripheral side to the inner peripheral side. The heights of the wrap walls 22E, 22F, 32E, and 32F may be gradually increased from the outer peripheral side to the inner peripheral side of the fixed scroll 30Z (in a stepped manner), or continuously increased and spiraled. You may form in a shape.

According to the configuration as described above, the compressor 10Z is configured such that the wrap heights L1 and L2 of the orbiting scroll 20Z and the fixed scroll 30Z are gradually reduced from the outer peripheral side toward the inner peripheral side. The cross section of the compression space formed between the fixed scroll 30Z is reduced not only in the radial direction but also in the height direction. As a result, the compression ratio of the compressor 10Z can be increased. Further, in the orbiting scroll 20Z and the fixed scroll 30Z, by increasing the height of the outer peripheral wrap walls 22E, 22F, 32E and 32F, the capacity of the orbiting scroll 20Z and the fixed scroll 30Z can be increased without increasing the outer diameter. Increase is possible. Thereby, further size reduction and capacity increase of the compressor 10Z can be achieved.
Moreover, in the orbiting scroll 20Z and the fixed scroll 30Z, the height of the central wrap walls 22E, 22F, 32E, and 32F where the load load due to compression is large can be suppressed, so the strength of the orbiting scroll 20Z and the fixed scroll 30Z is improved. And high reliability can be obtained.

  In addition, by forming compression spaces on both sides of the end plate 21 of the orbiting scroll 20Z, the compression load in the axial direction (thrust direction) of the main shaft 12 of the compressor 10Z can be balanced, and loss due to the thrust load is reduced. Can be suppressed.

  In addition, the wrap wall 22E on one side of the end plate 21 of the orbiting scroll 20Z, the wrap wall 22F on the other side, and the one wrap wall 32E and the other 32F of the fixed scroll 30Z have a spiral winding direction. In contrast, since the phases are axisymmetric, the compression forces in the direction perpendicular to the axis of the main shaft 12 are opposite to each other when the refrigerant is compressed in one compression space 50E and the other compression space 50F. When the refrigerant is compressed in one compression space 50E and the other compression space 50F, if the compression force in the direction orthogonal to the axis of the main shaft 12 is the same direction, in the present invention where the compression ratio is particularly high, the wrap wall 22E , 22F and the lap walls 32E and 32F tend to increase in tooth surface load, and it is necessary to increase the strength of each part to resist this. In contrast, in the present embodiment, when the refrigerant is compressed in one compression space 50E and the other compression space 50F, the compression forces in the directions perpendicular to the axis of the main shaft 12 are opposite to each other, so that the wrapping is performed. It is possible to avoid an increase in tooth load on the walls 22E and 22F and the wrap walls 32E and 32F.

  The configuration shown in the third embodiment can be combined with the first embodiment.

In each of the above embodiments, the compressors 10X, 10Y, and 10Z are vertical, but the present invention can be similarly applied to a case where the compressors are horizontal.
Further, the detailed structure of each part of the compressors 10X, 10Y, and 10Z can be changed as appropriate without departing from the gist of the present invention.
In addition to this, as long as it does not depart from the gist of the present invention, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.

  10X, 10Y, 10Z ... compressor, 11 ... housing, 12 ... main shaft, 12a ... lubricating oil flow path, 13 ... bearing, 20X, 20Y, 20Z ... orbiting scroll, 21 ... end plate, 22A, 22B, 22C, 22D, 22E, 22F ... Wrap wall (turning scroll side wrap wall), 23 ... Recess, 24 ... Drive bush (bearing), 30X, 30Y, 30Z ... Fixed scroll, 31A, 31B, 31C, 31E ... End plate, 32A, 32B, 32C, 32D, 32E, 32F ... wrap wall (fixed scroll side wrap wall), 50A, 50B, 50C, 50D, 50E, 50F ... compression space

Claims (6)

A scroll type compressor,
A main shaft rotatably supported in a housing forming an outer shell;
A orbiting scroll rotatably connected to a position offset with respect to the center of the main shaft;
A fixed scroll fixed to the housing and forming a compression space for compressing the refrigerant by facing the orbiting scroll;
The orbiting scroll has spiral-shaped orbiting scroll side wrap walls formed on both sides of a disk-shaped end plate, and the fixed scroll has the orbiting scroll side wrap formed on both sides of the end plate of the orbiting scroll. A pair of fixed scroll side wrap walls facing each of the walls are formed,
A concave portion is formed in a central portion on one surface side of the end plate of the orbiting scroll, and an eccentric boss provided eccentrically from a central axis of the main shaft at a tip portion of the main shaft is inserted into the concave portion via a bearing. The compressor characterized by having. The cross-sectional area of the compression space formed between the orbiting scroll and the fixed scroll is gradually reduced from the outer peripheral side toward the inner peripheral side,
2. The compressor according to claim 1, wherein a wrap height between the orbiting scroll side wrap wall and the fixed scroll side wrap wall is gradually reduced from an outer peripheral side toward an inner peripheral side.   In the orbiting scroll and the fixed scroll, the wrap height of the orbiting scroll side wrap wall and the fixed scroll side wrap wall formed on one side of the end plate, and the lap height formed on the other side of the end plate. The compressor according to claim 1 or 2, wherein a wrap height of the orbiting scroll side wrap wall and the fixed scroll side wrap wall are different from each other.   In the orbiting scroll and the fixed scroll, the orbiting scroll side wrap wall and the fixed scroll side wrap wall formed on one side of the end plate, and the orbiting scroll side formed on the other side of the end plate. The compressor according to any one of claims 1 to 3, wherein the wrap wall and the fixed scroll side wrap wall are spirally wound in different directions. A scroll type compressor,
A main shaft rotatably supported in a housing forming an outer shell;
A orbiting scroll rotatably connected to a position offset with respect to the center of the main shaft;
A fixed scroll fixed to the housing and forming a compression space for compressing the refrigerant by facing the orbiting scroll;
The orbiting scroll has spiral-shaped orbiting scroll side wrap walls formed on both sides of a disk-shaped end plate, and the fixed scroll has the orbiting scroll side wrap formed on both sides of the end plate of the orbiting scroll. A pair of fixed scroll side wrap walls facing each of the walls are formed,
The cross-sectional area of the compression space formed between the orbiting scroll and the fixed scroll is gradually reduced from the outer peripheral side toward the inner peripheral side,
The compressor characterized in that the wrap height between the orbiting scroll side wrap wall and the fixed scroll side wrap wall gradually decreases from the outer peripheral side toward the inner peripheral side.   In the orbiting scroll and the fixed scroll, the orbiting scroll side wrap wall and the fixed scroll side wrap wall formed on one side of the end plate, and the orbiting scroll side formed on the other side of the end plate. The compressor according to claim 5, wherein the wrap wall and the fixed scroll side wrap wall are spirally wound in different directions.

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