WO2019022134A1

WO2019022134A1 - Scroll compressor

Info

Publication number: WO2019022134A1
Application number: PCT/JP2018/027885
Authority: WO
Inventors: 二上　義幸; 悠介今井; 淳作田
Original assignee: パナソニックＩｐマネジメント株式会社
Priority date: 2017-07-27
Filing date: 2018-07-25
Publication date: 2019-01-31
Also published as: JP7022902B2; JPWO2019022134A1

Abstract

A compressor (1), wherein a flow-adjusting plate (160) provided inside a sealed container (10) is configured such that some of a refrigerant flowing in from an intake tube (13) flows to a compression-mechanism (170) side without colliding with the flow-adjusting plate (160), and the rest of the refrigerant taken in from the intake tube (13) collides with the flow-adjusting plate (160) and is diverted to an electric-motor (80) side.

Description

Scroll compressor

The present disclosure relates to scroll compressors.

In recent years, a partition plate has been provided in a compression container, and a low pressure side chamber partitioned by the partition plate is provided with a compression element having a fixed scroll and a turning scroll, and an electric element for turning the turning scroll. Sealed scroll compressors are known. In this type of sealed scroll compressor, the refrigerant sucked from the refrigerant suction pipe is compressed by the compression element, and the refrigerant compressed by the compression element is partitioned by the partition plate through the discharge port of the fixed scroll. It is discharged into the high pressure side chamber (see, for example, Patent Document 1).

FIG. 10 shows a scroll compressor described in Patent Document 1. As shown in FIG. The refrigerant is introduced into the low pressure space 201 in the closed container via the refrigerant suction pipe 200. At this time, in the scroll compressor, the refrigerant is branched by colliding with the straightening vane 202 provided at a portion facing the opening of the refrigerant suction pipe 200. Then, the electric element is cooled by a part of the introduced refrigerant, and the remaining refrigerant is sucked into the compression element and compressed.

However, in the above-described conventional configuration, when the refrigerant is branched by the rectifying plate 202, the flow direction of the refrigerant after colliding with the rectifying plate 202 and being diverted is parallel to the rotation axis (vertical direction in FIG. 10) Become. Therefore, the refrigerant that has flowed out from the straightening vane 202 to the opposite side to the electric element side collides with the partition plate 203. Since the partition plate 203 is in contact with the high pressure space 204, the temperature is high. Therefore, since the refrigerant is heated by coming into contact with the partition plate 203, there is a problem that the density of the refrigerant sucked into the compression mechanism portion 205 is lowered and the volumetric efficiency is lowered.

Unexamined-Japanese-Patent No. 4-255595

The present disclosure solves the problems as described above, and provides a highly efficient scroll compressor by preventing a decrease in volumetric efficiency due to heating of the sucked refrigerant.

Specifically, in the scroll compressor according to the present disclosure, a part of the refrigerant drawn from the suction pipe flows toward the compression mechanism without colliding with the straightening vane, and the remaining refrigerant drawn from the suction pipe The current plate is configured such that it collides with the current plate and is diverted to the motor side.

As a result, the remaining amount of refrigerant can be made to flow out directly to the compression mechanism side while the amount of refrigerant necessary to cool the electric motor flows out to the electric motor side by the straightening vanes. Therefore, it is possible to prevent the decrease in the efficiency of the compressor caused by the intake refrigerant being heated by the partition plate.

Sectional drawing which cut | disconnected the scroll compressor which concerns on Embodiment 1 of this indication longitudinally Sectional drawing which cut | disconnected the scroll compression which concerns on the Embodiment 1 longitudinally, when it sees from the axial center of a suction pipe. Side view of orbiting scroll of scroll compressor according to Embodiment 1 Sectional drawing which cut | disconnected the turning scroll in FIG. 2A by XX of FIG. 2A Bottom view of fixed scroll of scroll compressor according to Embodiment 1 of the present disclosure An exploded perspective view of the fixed scroll according to Embodiment 1 as viewed obliquely from above The perspective view which looked at the main bearing of the scroll compressor concerning the embodiment 1 obliquely from the top Top view of rotation suppression member of scroll compressor according to Embodiment 1 of the present invention Sectional view of the main part of the scroll compressor according to the first embodiment The perspective view which shows the cross section of the principal part of the scroll compressor concerning the embodiment 1 Sectional drawing which cut | disconnected the scroll compressor which concerns on Embodiment 2 of this indication longitudinally Sectional drawing which cut | disconnected the scroll compressor which concerns on the Embodiment 2 longitudinally, when it sees from the axial center of a suction pipe. Cross-sectional view of a conventional scroll compressor cut in the longitudinal direction

A scroll compressor according to an aspect of the present disclosure includes a closed container, a partition plate that divides the inside of the closed container into a high pressure space and a low pressure space, a fixed scroll adjacent to the partition plate, and a fixed scroll engaged with the fixed scroll. And a motor for driving the orbiting scroll, a rotation suppressing member for preventing rotation of the orbiting scroll, a main bearing for supporting the orbiting scroll, and an opening opening toward the low pressure space. It has an intake pipe, and a straightening vane which diverts the refrigerant drawn into the closed container from the intake pipe. The fixed scroll, the compression mechanism including the orbiting scroll and the rotation suppressing member, the motor, the current plate and the main bearing are disposed in the low pressure space, and the stationary scroll and the orbiting scroll are disposed between the partition plate and the main bearing. In the straightening vane, part of the refrigerant sucked from the suction pipe flows to the compression mechanism side without colliding with the straightening vane, and the remaining refrigerant sucked from the suction pipe collides with the straightening vane to the motor side. It is configured to be diverted.

In a scroll compressor according to another aspect of the present disclosure, the compression mechanism portion has a suction portion into which at least a portion of the refrigerant sucked from the suction pipe is sucked, and the opening area of the opening portion of the suction pipe is set to A Assuming that the area of the overlapping portion between the opening of the opening and the straightening vane when viewed from the axial center direction of the suction pipe is B, A> B, and the overlapping portion corresponds to the compression mechanism portion of the straightening vane It may be located on the suction side of the

According to this configuration, the refrigerant introduced from the suction pipe is diverted by the straightening vane. At this time, the amount of refrigerant necessary for cooling the motor is branched to the motor side, and the remaining refrigerant is directly discharged to the suction portion side of the compression mechanism portion, so the refrigerant in the partition plate having a relatively high temperature Collision is avoided. For this reason, the sucked refrigerant is directly sucked from the suction portion of the fixed scroll without being heated by the partition plate. Thus, it is possible to suppress the decrease in refrigerant density due to the refrigerant being heated, and to improve the efficiency of the scroll compressor.

The scroll compressor according to another aspect of the present disclosure may have a configuration in which a hole is provided at the overlapping portion of the straightening vane with the opening of the opening.

According to this configuration, it is possible to improve the efficiency of the scroll compressor by suppressing the decrease in the refrigerant density due to the refrigerant being heated by the simple configuration in which the holes are provided. Therefore, the positions of the suction pipe and the straightening vane do not have to be changed from the conventional scroll compressor.

In the scroll compressor according to another aspect of the present disclosure, the straightening vane may be provided so as to cover the left and right portions of the opening of the suction pipe as viewed from the axial center direction of the suction pipe.

According to this configuration, the refrigerant sucked from the suction pipe is prevented from being diverted from the opening of the opening portion in the left-right direction of the opening, that is, in the circumferential direction of the sealed container, and the refrigerant to the compression mechanism side and the motor side Can be efficiently discharged, and the refrigerant can be more efficiently introduced to the suction portion of the compression mechanism portion. Therefore, the contact of the refrigerant to the partition plate can be further reduced to suppress the decrease in the refrigerant density, and the efficiency of the scroll compressor can be improved.

In the scroll compressor according to another aspect of the present disclosure, at least a part of the opening of the suction pipe overlaps the suction section of the compression mechanism when viewed from the axial center direction of the suction pipe. May be configured.

According to this configuration, the refrigerant sucked from the suction pipe is sucked from the suction portion of the compression mechanism portion, which is disposed at a linear position with respect to the opening of the suction pipe. For this reason, it is possible to further reduce the contact of the refrigerant to the partition plate, to suppress the decrease in the refrigerant density, and to improve the efficiency of the scroll compressor.

In the scroll compressor according to another aspect of the present disclosure, when the diameter of the opening of the suction pipe is d, the distance between the suction pipe and the straightening vane may be larger than d / 2 and smaller than d. .

According to this configuration, the pressure loss of the refrigerant flowing between the straightening vane and the inner wall surface of the hermetic container can be reduced, so the effect of the diversion by the straightening vane can be increased. Therefore, the efficiency of the scroll compressor can be improved.

In the scroll compressor according to another aspect of the present disclosure, the area B of the overlapping portion between the opening of the opening and the straightening vane when viewed from the axial center direction of the suction pipe is 30% of the opening area A of the opening It may be configured to be larger than 70%.

According to this configuration, the refrigerant can be diverted to an appropriate amount for each of the compressor side and the motor side, and the efficiency of the compression mechanism can be improved while efficiently cooling the motor.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited by the following embodiments.

Embodiment 1
[1. Overall configuration of scroll compressor]
FIG. 1A is a cross-sectional view in which the scroll compressor according to the first embodiment is cut in the longitudinal direction. FIG. 1B is a cross-sectional view of the scroll compression according to the first embodiment, cut in the vertical direction when viewed from the axial center of the suction pipe.

The compressor 1 is equipped with the cylindrical airtight container 10 long to an up-down direction as an outer shell, as shown to FIG. 1A and 1B. In the present specification, the vertical direction is the Z-axis direction (the rotational axis direction of the motor) in each drawing.

The compressor 1 is a sealed scroll compressor including a compression mechanism portion 170 for compressing a refrigerant and an electric motor 80 for driving the compression mechanism portion 170 inside the sealed container 10. The compression mechanism portion 170 is constituted by at least a fixed scroll 30, a orbiting scroll 40, a main bearing 60, and an Oldham ring 90 which is a rotation control member.

Above the closed container 10, a partition plate 20 is provided which divides the inside of the closed container 10 into upper and lower parts. The partition plate 20 divides the space inside the closed container 10 into a high pressure space 11 and a low pressure space 12. The high pressure space 11 is a space filled with a high pressure refrigerant after being compressed by the compression mechanism section 170, and the low pressure space 12 is a space filled with a low pressure refrigerant before being compressed by the compression mechanism section 170. At the bottom of the low pressure space 12 is formed an oil reservoir 15 in which lubricating oil is stored.

In the closed container 10, a refrigerant suction pipe (hereinafter referred to as a suction pipe) 13 connecting the outside of the closed container 10 with the low pressure space 12 and a refrigerant discharge pipe 14 connecting the outside of the closed container 10 with the high pressure space 11 It is connected.

In the compressor 1, a low pressure refrigerant is introduced to the low pressure space 12 from a refrigeration cycle circuit (not shown) provided outside the closed container 10 via the suction pipe 13. Further, the high pressure refrigerant compressed by the compression mechanism section 170 is introduced into the high pressure space 11 and then discharged from the high pressure space 11 via the refrigerant discharge pipe 14 into the refrigeration cycle circuit.

Further, in the sealed container 10, a flow straightening plate 160 for dividing the refrigerant sucked from the suction pipe 13 is provided as described below.

[2. Configuration of current plate]
A flow straightening plate 160 is attached to the inner wall surface of the closed vessel 10 so as to face the closed vessel inner opening (hereinafter referred to as an opening) 13 a of the suction pipe 13. The upper side of the baffle plate 160 is closed. That is, the baffle plate 160 is configured such that the refrigerant sucked from the suction pipe 13 does not flow out from the upper side in the vertical direction. In the straightening vane 160 and the suction pipe 13, a part of the refrigerant sucked from the suction pipe 13 flows toward the compression mechanism portion 170 without colliding with the straightening vane 160, and the remaining refrigerant sucked from the suction pipe 13 is straightening vane It is configured to collide with 160 and be diverted to the motor 80 side.

Specifically, as shown in FIG. 1B, the opening area of the opening 13a of the suction pipe 13 is A, and the opening of the opening 13a of the suction pipe 13 and the rectifying plate 160 when viewed from the axial center direction of the suction pipe 13. Assuming that the area of the overlapping portion with B is B, A> B, and the overlapping portion corresponds to the suction portion of the compression mechanism portion 170 (in the present embodiment, the suction portion 38 of the fixed scroll 30) Provided on the) side.

In FIG. 1B, the opening of the opening 13a is a circular area indicated by a vertical line. In addition, the overlapping portion is a partial area of the above-described circle indicated by both vertical and horizontal lines.

Further, in the present embodiment, as shown in FIG. 1B, the current plate 160 is configured to cover the left and right portions (the end portions in the circumferential direction of the sealed container 10) of the opening 13a of the suction pipe 13.

Furthermore, the straightening vane 160 is configured such that at least a part of the opening 13 a of the suction pipe 13 overlaps the suction portion 38 of the fixed scroll 30 when viewed from the axial center direction of the suction pipe 13 There is.

When the diameter of the opening 13a of the suction pipe 13 is d, the distance between the suction pipe 13 and the straightening vane 160 is larger than d / 2 and smaller than d.

Furthermore, the area B of the overlapping portion where the opening of the opening 13a of the suction pipe 13 and the flow straightening plate 160 overlap is in the range of more than 30% and less than 70% of the opening area A of the opening 13a of the suction pipe 13 It is configured.

[3. Configuration of compression mechanism section]
As shown in FIG. 1A, the compressor 1 includes a compression mechanism section 170 in the low pressure space 12 in the closed vessel 10. The compression mechanism section 170 has a fixed scroll 30 and a orbiting scroll 40.

The fixed scroll 30 is a non-orbiting scroll. The fixed scroll 30 is disposed below the partition plate 20 adjacent to the partition plate 20. The orbiting scroll 40 is disposed below the fixed scroll 30 in mesh with the fixed scroll 30.

The fixed scroll 30 includes a disk-shaped fixed scroll end plate 31 and a spiral fixed spiral wrap 32 erected on the lower surface of the fixed scroll end plate 31.

The orbiting scroll 40 includes a disc-shaped orbiting scroll end plate 41, a spiral orbiting scroll wrap 42 provided on the upper surface of the orbiting scroll end plate 41, and a lower boss portion 43. The lower boss portion 43 is a cylindrical protrusion formed substantially at the center of the lower surface of the orbiting scroll end plate 41.

A compression chamber 50 is formed between the orbiting scroll 40 and the fixed scroll 30 by meshing the orbiting spiral wrap 42 of the orbiting scroll 40 and the fixed spiral wrap 32 of the fixed scroll 30. The compression chamber 50 is formed on the inner wall (described later) side of the swirling and spiral wrap 42 and the outer wall (described later) side.

Below the fixed scroll 30 and the orbiting scroll 40, a main bearing 60 for supporting the orbiting scroll 40 is provided. The main bearing 60 includes a boss housing portion 62 provided substantially at the center of the upper surface of the main bearing 60 and a bearing portion 61 provided below the boss housing portion 62. The boss accommodating portion 62 is a recess for accommodating the lower boss portion 43. The upper portion of the bearing portion 61 is opened as a boss accommodating portion 62, and the lower portion of the bearing portion 61 is opened to the low pressure space 12 as a through hole.

The main bearing 60 supports the orbiting scroll 40 on the upper surface of the main bearing 60, and supports the rotating shaft 70 at the bearing portion 61.

As shown in FIGS. 1A and 1B, the rotating shaft 70 has the vertical direction as an axis. One end side of the rotating shaft 70 is pivotally supported by the bearing portion 61, and the other end side is pivotally supported by the auxiliary bearing 16.

The auxiliary bearing 16 is provided below the low pressure space 12, preferably in the oil reservoir 15. At the upper end of the rotating shaft 70, an eccentric shaft 71 eccentric to the axial center of the rotating shaft 70 is provided.

The eccentric shaft 71 is slidably inserted in the lower boss portion 43 via the swing bush 78 and the pivot bearing 79. The lower boss portion 43 is rotationally driven by the eccentric shaft 71.

An oil passage 72 through which the lubricating oil passes is formed in the rotating shaft 70. The oil passage 72 is a through hole formed in the axial direction of the rotating shaft 70. One end of the oil passage 72 opens into the oil reservoir 15 as a suction port 73 provided at the lower end of the rotary shaft 70. At the upper part of the suction port 73, a paddle 74 for pumping the lubricating oil from the suction port 73 to the oil passage 72 is provided.

The rotating shaft 70 is coupled to the motor 80. The motor 80 is disposed between the main bearing 60 and the sub bearing 16. The electric motor 80 includes a stator 81 fixed to the sealed container 10 and a rotor 82 disposed inside the stator 81.

The rotating shaft 70 is fixed to the rotor 82. The rotating shaft 70 includes a balance weight 17 a provided above the rotor 82 and a balance weight 17 b provided below. The balance weight 17 a and the balance weight 17 b are disposed at positions shifted by 180 ° in the circumferential direction of the rotation shaft 70 in plan view.

The rotating shaft 70 rotates in balance with the centrifugal force generated by the balance weight 17 a and the balance weight 17 b and the centrifugal force generated by the revolving motion of the orbiting scroll 40. The balance weight 17 a and the balance weight 17 b may be provided on the rotor 82.

An Oldham ring 90 which is a rotation suppressing member is provided between the orbiting scroll 40 and the main bearing 60. The Oldham ring 90 prevents rotation of the orbiting scroll 40. Thus, the orbiting scroll 40 pivots with respect to the fixed scroll 30 without rotating.

The fixed scroll 30, the orbiting scroll 40, the motor 80, the Oldham ring 90 and the main bearing 60 are disposed in the low pressure space 12. The fixed scroll 30 and the orbiting scroll 40 are disposed between the partition plate 20 and the main bearing 60.

The partition plate 20 and the main bearing 60 are fixed to the closed container 10. An elastic body (not shown) is provided on one of the fixed scroll 30 and the orbiting scroll 40. Then, at least one of the fixed scroll 30 and the orbiting scroll 40 provided with the elastic body is axially movably provided in at least a part of a section between the partition plate 20 and the main bearing 60 . The at least one section is, for example, between the partition plate 20 and the orbiting scroll 40 or between the fixed scroll 30 and the main bearing 60.

In the present embodiment, the fixed scroll 30 is provided movably in the axial direction (vertical direction in FIG. 1) with respect to the columnar member 100 provided in the main bearing 60. The lower end portion of the columnar member 100 is inserted and fixed in the bearing side hole portion 102, and the upper end portion is slidably inserted in the scroll side hole portion 101.

The columnar member 100 restricts the rotation and radial movement of the fixed scroll 30 and allows axial movement of the fixed scroll 30. That is, the fixed scroll 30 is supported by the main bearing 60 by the columnar member 100, and a partial section between the partition plate 20 and the main bearing 60, more specifically, between the partition plate 20 and the orbiting scroll 40 It is provided to be movable in the axial direction.

A plurality of columnar members 100 are provided, and are arranged at predetermined intervals in the circumferential direction. Desirably, the plurality of columnar members 100 are arranged substantially equally in the circumferential direction.

The columnar member 100 may be provided on the fixed scroll 30. That is, the lower end portion of the columnar member 100 may be slidably inserted in the bearing side hole portion 102, and the upper end portion may be inserted and fixed in the scroll side hole portion 101.

[4. Operation and Action]
Next, the operation and action of the compressor 1 configured as described above will be described.

When the motor 80 is driven, the rotary shaft 70 rotates with the rotor 82. The orbiting scroll 40 pivots around the central axis of the rotating shaft 70 without rotating on its axis by the eccentric shaft 71 and the Oldham ring 90. As a result, the volume of the compression chamber 50 is reduced, and the refrigerant in the compression chamber 50 is compressed.

The refrigerant in the refrigeration cycle circuit is introduced from the suction pipe 13 into the low pressure space 12. Then, the refrigerant introduced into the low pressure space 12 collides with the rectifying plate 160 and is diverted.

In the present embodiment, as shown in FIG. 1B, the suction pipe 13 and the flow straightening plate 160 have an area A of the opening 13a of the suction pipe 13 and an opening of the opening 13a when viewed from the axial center of the suction pipe 13. Assuming that the area of the overlapping portion of the straightening vane 160 is B, A> B, and the overlapping portion is provided on the suction portion 38 side of the fixed scroll 30 in the straightening vane 160.

Therefore, the refrigerant introduced from the suction pipe 13 collides with the overlapping portion of the straightening vane 160 and a part thereof is diverted to the motor 80 side, and the rest passes through the opening 13 a of the suction pipe 13, It flows directly to the compression mechanism section 170 side. That is, only the amount of refrigerant necessary to cool the electric motor 80 is diverted to the electric motor 80 side, and the remaining refrigerant directly flows out to the suction portion 38 side of the fixed scroll 30 in the compression mechanism portion 170. In other words, the remaining refrigerant flows toward the suction portion 38 of the compression mechanism portion 170 and is sucked from the suction portion 38 while the collision with the partition plate 20 having a relatively high temperature is suppressed. Therefore, the refrigerant sucked from the suction pipe 13 can be prevented from being heated by the partition plate 20, and the decrease in refrigerant density due to the refrigerant being heated can be suppressed. Thereby, the efficiency of the scroll compressor can be improved.

Further, in the present embodiment, the straightening vane 160 is a left and right portion of the opening 13a of the suction pipe 13 (a portion in the circumferential direction of the sealed container 10 in the opening 13a) when viewed from the axial center direction of the suction pipe 13. ) Is provided to cover the

As a result, the refrigerant sucked from the suction pipe 13 is prevented from being diverted from the opening 13a of the suction pipe 13 in the left-right direction, that is, the circumferential direction of the sealed container 10, and the compression mechanism 170 side and the electric motor 80 side. Can be diverted efficiently. Therefore, the refrigerant is more efficiently introduced to the suction portion 38 of the compression mechanism portion 170. Therefore, the contact of the refrigerant with the partition plate 20 can be further reduced, the decrease in refrigerant density can be suppressed, and the efficiency of the scroll compressor can be improved.

Furthermore, in the present embodiment, at least a part of the opening of the opening 13a of the suction pipe 13 overlaps the suction 38 of the fixed scroll 30 when viewed from the axial center direction of the suction pipe. There is.

Thus, the suction refrigerant flowing through the part of the opening 13 a of the suction pipe 13 linearly travels to the suction portion 38 of the compression mechanism 170. Therefore, the refrigerant can be directly sucked into the suction portion 38 of the compression mechanism portion 170 more efficiently. Therefore, the refrigerant can be prevented from coming into contact with the partition plate 20, and the decrease in the refrigerant density can be suppressed, and the efficiency of the scroll compressor can be improved.

Further, in the present embodiment, assuming that the diameter of the opening 13a of the suction pipe 13 is d, the distance between the suction pipe 13 and the straightening vane 160 is in a range larger than d / 2 and smaller than d.

By setting the distance between the suction pipe 13 and the straightening vane 160 to be larger than d / 2, the pressure loss of the refrigerant in the straightening vane 160 (between the straightening vane 160 and the inner wall surface of the sealed container 10) can be reduced. . Further, since the distance between the suction pipe 13 and the straightening vane 160 is smaller than d, the sucked refrigerant is likely to be diverted to the motor 80 by the straightening vane 160. That is, since the pressure loss of the refrigerant flowing between the straightening vane 160 and the inner wall surface of the sealed container 10 can be reduced, the refrigerant can be efficiently diverted to the motor 80 side and the compression mechanism portion 170 side. Thus, the efficiency of the scroll compressor can be improved.

Further, in the present embodiment, the area B of the overlapping portion of the opening 13 a of the suction pipe 13 and the flow straightening plate 160 is within the range of more than 30% and less than 70% of the opening area A of the opening 13 a of the suction pipe 13. It is.

By configuring the area B of the overlapping portion to be larger than 30% of the opening area A of the opening 13 a of the refrigerant suction pipe 13, it is possible to secure the amount of refrigerant diverted to the motor 80 to an appropriate amount. And the motor 80 can be cooled well.

Further, by configuring the area B of the overlapping portion to be smaller than 70% of the opening area A of the opening 13a of the suction pipe 13, the amount of refrigerant diverted to the compression mechanism 170 side can also be secured to an appropriate amount. The compression mechanism unit 170 can perform compression well.

That is, the refrigerant can be favorably compressed by the compression mechanism section 170 while the motor 80 is well cooled. The refrigerant sucked from the suction pipe 13 is directly sucked from the suction portion 38 of the compression mechanism portion 170 without colliding with the partition plate 20 having a relatively high temperature to be heated, so the compression mechanism portion The compression efficiency of the refrigerant at 170 can be improved.

The refrigerant compressed in the compression chamber 50 is discharged from the refrigerant discharge pipe (discharge pipe) 14 via the high pressure space 11.

Further, the lubricating oil stored in the oil reservoir 15 is pumped up from the suction port 73 along the paddle 74 to the upper side of the oil passage 72 by the rotation of the rotating shaft 70.

The pumped lubricating oil is supplied from the first fuel inlet 75, the second fuel inlet 76, and the third fuel inlet 77 to the bearing portion 61, the sub bearing 16, and the boss housing portion 62, respectively. Further, the lubricating oil pumped up to the boss housing portion 62 is guided to the sliding surface between the main bearing 60 and the orbiting scroll 40, and is discharged through the return path 63 (see FIG. 5) to return to the oil reservoir 15 again. .

[5. Detailed configuration of compressor]
The detailed configuration of the compressor 1 will be further described.

FIG. 2A is a side view of the orbiting scroll of the scroll compressor according to the present embodiment. FIG. 2B is a cross-sectional view of the orbiting scroll in FIG. 2A cut along the line XX in FIG. 2A.

The swirling spiral wrap 42 shown in FIG. 2A has an involute curve-like cross section in which the starting end 42a located on the center side of the orbiting scroll end plate 41 is wounded and the radius is gradually expanded toward the end 42b located on the outer peripheral side. (See FIG. 2B). The swirling spiral wrap 42 has a predetermined height (vertical length) and a predetermined wall thickness (radial length of the swirling spiral wrap 42).

At both ends of the lower surface of the orbiting scroll end plate 41, a pair of first key grooves 91 configured to extend in the direction from the outer peripheral side toward the center side are provided (see FIG. 2B).

FIG. 3 is a bottom view of the fixed scroll of the scroll compressor according to the present embodiment. FIG. 4 is an exploded perspective view of the fixed scroll as viewed obliquely from above.

As shown in FIG. 3, the fixed spiral wrap 32 is an involute curve having a starting end 32 a located on the center side of the fixed scroll end plate 31 as a winding start and gradually expanding a radius toward the end 32 c located on the outer peripheral side. Wall having a cross section of The fixed spiral wrap 32 has a predetermined height (vertical length) equal to the turning spiral wrap 42 and a predetermined wall thickness (radial length of the fixed spiral wrap 32).

The fixed spiral wrap 32 has an inner wall (wall on the center side) and an outer wall (wall on the outer circumference) from the start end 32a to the middle portion 32b, and only an inner wall from the middle portion 32b to the end 32c.

As shown in FIGS. 3 and 4, a first discharge port 35 is formed substantially at the center of the fixed scroll end plate 31. Further, a bypass port 36 and an intermediate pressure port 37 are formed in the fixed scroll end plate 31. The bypass port 36 is disposed in the vicinity of the first discharge port 35 in a region where the refrigerant at a high pressure immediately before the completion of the compression exists.

The bypass port 36 includes a bypass port 36 communicating with the compression chamber 50 formed on the outer wall side of the orbiting spiral wrap 42 (see FIG. 2B) with one set of three small holes, and on the inner wall side of the orbiting spiral wrap 42 Two sets of bypass ports 36 are provided which communicate with the compression chamber 50 being formed. The medium pressure port 37 is disposed in the vicinity of the middle portion 32 b in a region where a refrigerant at a middle pressure during compression is present.

As shown in FIG. 4, a pair of first flanges 34 a and a pair of second flanges 34 b are provided on the outer peripheral portion of the fixed scroll 30 so as to protrude outward from the peripheral wall 33. The first flange 34 a and the second flange 34 b are provided below the fixed scroll end plate 31 (on the side of the orbiting scroll 40). The second flange 34b is provided below the first flange 34a, and the lower surface (the surface on the side of the orbiting scroll 40) of the second flange 34b is positioned substantially flush with the tip surface of the fixed spiral wrap 32. .

Each of the pair of first flanges 34 a is substantially equally spaced in the circumferential direction of the rotation shaft 70 at a predetermined interval. Further, each of the pair of second flanges 34 b is arranged substantially equally spaced in the circumferential direction of the rotation shaft 70 at a predetermined interval.

A suction portion 38 for taking the refrigerant into the compression chamber 50 is formed on the peripheral wall 33 of the fixed scroll 30.

Further, the first flange 34a is provided with the scroll side hole 101 into which the upper end portion of the columnar member 100 (see FIG. 1) is inserted. The scroll side holes 101 are provided one by one in each of the pair of first flanges 34 a. The two scroll side holes 101 are arranged at predetermined intervals in the circumferential direction. Desirably, two scroll side hole parts 101 are equally arranged by the peripheral direction. The scroll side hole portion 101 may not be a through hole, and may be a concave portion recessed from the lower surface side.

The scroll side hole portion 101 communicates with the outside of the fixed scroll 30, that is, the low pressure space 12 by a communication hole (not shown).

The second flange 34b is provided with a second key groove 92 (see FIG. 3). The second key groove 92 is a pair of grooves provided in the pair of second flanges 34 b one by one and configured to be long in the direction from the outer peripheral side to the center side.

As shown in FIG. 4, an upper boss 39 is provided at the center of the upper surface (the surface on the side of the partition plate 20) of the fixed scroll 30. The upper boss portion 39 is a cylindrical protrusion that protrudes from the upper surface of the fixed scroll 30. The first discharge port 35 and the bypass port 36 open on the upper surface of the upper boss portion 39. A discharge space 30H is formed between the upper boss 39 and the partition plate 20 on the upper surface side of the upper boss 39 (see FIG. 7 described later). The first discharge port 35 and the bypass port 36 communicate with the discharge space 30H.

Further, a ring-shaped convex portion 310 is provided on the outer peripheral side of the upper boss portion 39 on the upper surface of the fixed scroll 30. A recess is formed on the upper surface of the fixed scroll 30 by the upper boss 39 and the ring-shaped protrusion 310. The recess forms an intermediate pressure space 30M (see FIG. 7 described later). The medium pressure port 37 opens on the upper surface (bottom surface of the recess) of the fixed scroll 30 and communicates with the medium pressure space 30M.

The pore size of the medium pressure port 37 is less than the wall thickness of the swirl wrap 42. As a result, the communication between the compression chamber 50 formed on the inner wall side of the orbiting spiral wrap 42 and the compression chamber 50 formed on the outer wall side of the orbiting spiral wrap 42 is prevented.

A bypass check valve 121 for opening and closing the bypass port 36 and a bypass check valve stop 122 for preventing excessive deformation of the bypass check valve 121 are provided on the upper surface of the upper boss portion 39. By using a reed valve as the bypass check valve 121, the height can be reduced. In addition, a V-shaped reed valve is used as the bypass check valve 121, so that a bypass port 36 communicating with the compression chamber 50 formed on the outer wall side of the swirl spiral wrap 42 and an inner wall side of the swirl spiral wrap 42 The bypass port 36 communicating with the compression chamber 50 formed in can be opened and closed by one reed valve.

A medium pressure non-return valve (not shown) that allows the medium pressure port 37 to be opened and closed, and a medium pressure nonreturn valve that prevents excessive deformation of the medium pressure check valve on the upper surface (bottom surface of the recess) of the fixed scroll 30 A valve stop (not shown) is provided. The size in the height direction can be made compact by using a reed valve as the medium pressure check valve. The medium pressure check valve can also be configured by a ball valve and a spring.

FIG. 5 is a perspective view of the main bearing of the scroll compressor according to the present embodiment as viewed obliquely from above.

As shown in FIG. 5, a bearing side hole portion 102 into which the lower end portion of the columnar member 100 (see FIG. 1) is inserted is provided on the outer peripheral portion of the main bearing 60. Two bearing side holes 102 are provided at predetermined intervals in the circumferential direction. Desirably, two bearing side hole parts 102 are equally distributed by the circumferential direction. The bearing side hole 102 may not be a through hole, but may be a recess recessed from the upper surface side.

A return path 63 is formed in the main bearing 60. One end of the return path 63 opens to the boss accommodating portion 62, and the other end opens to the lower surface of the main bearing 60. Note that one end of the return path 63 may be open at the upper surface of the main bearing 60. Further, the other end of the return path 63 may be open at the side surface of the main bearing 60.

The return path 63 also communicates with the bearing side hole 102. Accordingly, lubricating oil is supplied to the bearing side hole 102 by the return path 63.

FIG. 6 is a plan view showing an Oldham ring which is a rotation suppression member of the scroll compressor according to the present embodiment.

As shown in FIG. 6, the Oldham ring 90 includes a substantially annular ring portion 95, and a pair of first keys 93 and a pair of second keys 94 protruding from the upper surface of the ring portion 95. The first key 93 and the second key 94 are provided such that the straight line connecting the two first keys 93 and the straight line connecting the two second keys 94 are orthogonal to each other.

The first key 93 engages with the first key groove 91 (see FIG. 2B) of the orbiting scroll 40, and the second key 94 with the second key groove 92 of the fixed scroll 30 (see FIG. 3). Engage. As a result, the orbiting scroll 40 can pivot with respect to the fixed scroll 30 without rotating.

In the present embodiment, the fixed scroll 30, the orbiting scroll 40, and the oldham ring 90 are arranged in the order from the top in the axial direction of the rotating shaft 70 (see FIG. 1). For this reason, the first key 93 and the second key 94 are formed in the same plane in the ring portion 95. This makes it possible to process the first key 93 and the second key 94 from the same direction when creating the Oldham ring 90, and to reduce the number of times the Oldham ring 90 is detached from the processing apparatus. Therefore, the processing accuracy of the Oldham ring 90 can be improved and the processing cost can be reduced.

FIG. 7 is a cross-sectional view of the main part of the scroll compressor according to the present embodiment. FIG. 8 is a perspective view showing the cross section of the main part of the scroll compressor according to the present embodiment.

As shown in FIG. 7, the second discharge port 21 is provided at the center of the partition plate 20. A discharge check valve 131 for opening and closing the second discharge port 21 and a discharge check valve stop 132 for preventing excessive deformation of the discharge check valve 131 are provided on the upper surface of the partition plate 20. .

A discharge space 30H is formed between the partition plate 20 and the fixed scroll 30. The discharge space 30H communicates with the compression chamber 50 by the first discharge port 35 and the bypass port 36, and communicates with the high pressure space 11 by the second discharge port 21.

Since the discharge space 30H communicates with the high pressure space 11 via the second discharge port 21, a back pressure is applied to the upper surface side of the fixed scroll 30. That is, the fixed scroll 30 is pressed against the orbiting scroll 40 by the application of high pressure to the discharge space 30H. For this reason, the gap between the fixed scroll 30 and the orbiting scroll 40 can be eliminated, and the compressor 1 can perform highly efficient operation.

The plate thickness of the discharge check valve 131 is larger than the plate thickness of the bypass check valve 121. Thus, the discharge check valve 131 can be prevented from opening earlier than the bypass check valve 121.

The volume of the second discharge port 21 is larger than the volume of the first discharge port 35. Thereby, the pressure loss of the refrigerant discharged from the compression chamber 50 can be reduced.

Also, a taper may be formed on the inflow side of the second discharge port 21. This can further reduce pressure loss.

On the lower surface of the partition plate 20, an annular projecting portion 22 is provided around the second discharge port 21. The protrusion 22 is provided with a plurality of holes 221 into which a part of the closing member 150 described later is inserted.

As shown in FIGS. 7 and 8, the protrusion 22 is provided with a first seal member 141 and a second seal member 142. The first seal member 141 is a ring-shaped seal member that protrudes from the protrusion 22 toward the center of the partition plate 20. The tip of the first seal member 141 is in contact with the side surface of the upper boss 39. That is, the first seal member 141 is disposed in a gap between the partition plate 20 and the fixed scroll 30 and on the outer periphery of the discharge space 30H.

The second seal member 142 is a ring-shaped seal member that protrudes from the protrusion 22 toward the outer peripheral side of the partition plate 20. The second seal member 142 is disposed outside the first seal member 141. The tip of the second seal member 142 is in contact with the inner side surface of the ring-shaped convex portion 310. That is, the second seal member 142 is disposed between the partition plate 20 and the fixed scroll 30 in a gap located on the outer periphery of the intermediate pressure space 30M.

In other words, the discharge space 30H and the medium pressure space 30M are formed between the partition plate 20 and the fixed scroll 30 by the first seal member 141 and the second seal member 142. The discharge space 30H is a space formed on the upper surface side of the upper boss portion 39, and the medium pressure space 30M is a space formed on the outer peripheral side of the upper boss portion 39.

The first seal member 141 is a seal member that divides the discharge space 30H and the medium pressure space 30M, and the second seal member 142 is a seal member that divides the medium pressure space 30M and the low pressure space 12.

As the first seal member 141 and the second seal member 142, for example, polytetrafluoroethylene, which is a fluorocarbon resin, is suitable in terms of sealability and assembly. Furthermore, the reliability of the seal is improved by using, as the first seal member 141 and the second seal member 142, a material in which a fiber material is mixed with a fluorine resin.

The first seal member 141 and the second seal member 142 are sandwiched between the closing member 150 and the projection 22. Therefore, after the first seal member 141, the second seal member 142, and the closing member 150 are assembled to the partition plate 20, they can be disposed in the sealed container 10. As a result, the number of parts of the compressor 1 can be reduced and the assembly of the compressor 1 becomes easy.

More specifically, the closing member 150 includes a ring-shaped portion 151 disposed to face the protruding portion 22 of the partition plate 20 and a plurality of protruding portions 152 protruding from one surface of the ring-shaped portion 151.

The outer peripheral side of the first seal member 141 is sandwiched between a portion on the inner peripheral side of the upper surface of the ring-shaped portion 151 and the lower surface of the protrusion 22. Further, the inner peripheral side of the second seal member 142 is sandwiched between the outer peripheral portion of the upper surface of the ring-shaped portion 151 and the lower surface of the projecting portion 22.

That is, the ring-shaped portion 151 is opposed to the lower surface of the protruding portion 22 of the partition plate 20 via the first seal member 141 and the second seal member 142.

The plurality of protrusions 152 are inserted into the plurality of holes 221 formed in the protrusion 22. The upper end of the protrusion 152 is crimped so that the ring-shaped portion 151 is pressed against the lower surface of the protrusion 22. That is, the closing member 150 is fixed to the partition plate 20 such that the ring-shaped portion 151 is pressed against the lower surface of the projecting portion 22 by deforming the upper end of the projecting portion 152 into a flat plate shape. The closing member 150 is easily crimped by being formed of an aluminum material.

In a state where the first seal member 141 and the second seal member 142 are attached to the partition plate 20, the inner peripheral portion of the first seal member 141 protrudes from the ring-shaped portion 151 toward the center of the partition plate 20, The outer peripheral portion of the second seal member 142 protrudes from the ring-shaped portion 151 toward the outer peripheral side of the partition plate 20.

Then, the partition plate 20 to which the first seal member 141 and the second seal member 142 are attached is mounted in the sealed container 10, so that the portion on the inner circumferential side of the first seal member 141 corresponds to that of the fixed scroll 30. The portion on the outer peripheral side of the second seal member 142 is pressed against the inner peripheral surface of the ring-shaped convex portion 310 of the fixed scroll 30 while being pressed against the outer peripheral surface of the upper boss portion 39.

The medium pressure space 30 </ b> M communicates with the region of the compression chamber 50 in the middle of compression in which the refrigerant at the intermediate pressure exists, by means of the medium pressure port 37. For this reason, the pressure of the medium pressure space 30M is lower than the pressure of the discharge space 30H and higher than the pressure of the low pressure space 12.

Thus, in addition to the discharge space 30H, the intermediate pressure space 30M is formed between the partition plate 20 and the fixed scroll 30, so that adjustment of the pressing force of the fixed scroll 30 to the orbiting scroll 40 is easy. Become.

Further, since the medium pressure space 30M is formed by the first seal member 141 and the second seal member 142, the refrigerant leaks from the discharge space 30H to the medium pressure space 30M, and from the medium pressure space 30M to the low pressure space 12. Leakage of refrigerant can be reduced.

Second Embodiment
FIG. 9A is a cross-sectional view in which the scroll compressor according to the present embodiment is cut in the longitudinal direction. FIG. 9B is a cross-sectional view of the scroll compressor according to the present embodiment, cut in the vertical direction when viewed from the axial center of the suction pipe.

In the present embodiment, as shown in FIG. 9B, a hole is formed in the overlapping portion of the opening 13a of the suction pipe 13 and the flow control plate 160 in the flow control plate 160 when viewed from the axial center direction of the suction pipe 13. 160a is provided.

The other configuration is the same as that of the compressor 1 according to the first embodiment shown in FIG. 1 and, therefore, the same configuration as the configuration described in FIG.

According to the above configuration, a part of the refrigerant sucked from the suction pipe 13 is diverted in the direction of the suction portion 38 of the fixed scroll 30 in the compression mechanism portion 170 through the hole portion 160 a of the straightening vane 160. Further, the remaining refrigerant collides with a portion other than the hole portion 160 a of the straightening vane 160 and is diverted to the motor 80 side.

Therefore, if the size of the hole 160a satisfies the relationship between the opening area A and the area B of the overlapping portion described in the first embodiment, the same effect as that of the first embodiment can be obtained. As a result, the positional relationship between the suction pipe 13 and the straightening vane 160 can be simply processed by adding holes to the configuration of the existing compressor without changing, for example, shifting up and down. Similarly to the above, the reduction of the refrigerant density can be suppressed, and the efficiency of the compressor can be improved.

As described above, according to the present disclosure, it is possible to prevent a decrease in compression efficiency due to the refrigerant sucked in at the partition plate being heated, while securing the cooling performance for the motor. Thus, a scroll compressor with high efficiency can be provided. Therefore, it can be widely applied as a compressor of a refrigeration cycle apparatus such as a water heater, a hot water heater, an air conditioner, and the like.

1 compressor 10 sealed container 11 high pressure space 12 low pressure space 13 refrigerant suction pipe (suction pipe)
13a Sealed container inner opening (opening)
14 refrigerant discharge pipe (discharge pipe)
16 secondary bearing

17a balance weight

17b balance weight 20 partition plate 21 second discharge port 22 protrusion 30 fixed scroll 30H discharge space 30M medium pressure space 31 fixed scroll end plate 32 fixed scroll wrap 32a start end 32b middle part 32c end 33 peripheral wall 34a flange 34b Flange 35 first discharge port 36 bypass port 37 medium pressure port 38 suction portion 39 upper boss portion 40 orbiting scroll 42 orbiting scroll wrap 42a start end 42b end 43 lower boss portion 50 compression chamber 60 main bearing 61 bearing portion 62 boss housing portion 63 Return path 70 Rotating shaft 71 Eccentric shaft 72 Oil passage 73 Suction port 74 Paddle 75 Fuel port 76 Fuel port 80 Motor port 81 Motor 82 Stator 82 Rotor 90 Rotation suppressing member (Oldham ring)
91 key groove 92 key groove 93 first key 94 key 100 columnar member 101 scroll side hole 102 bearing side hole 121 bypass check valve 122 bypass check valve stop 131 discharge check valve 132 discharge check valve stop 141 seal Member 142 Sealing member 150 Closing member 151 Ring-shaped portion 152 Protruding portion 160 Flow straightening plate 160a Hole portion 170 Compression mechanism portion 221 Hole portion

Claims

A closed container,
A partition plate which divides the inside of the closed container into a high pressure space and a low pressure space;
A stationary scroll adjacent to the divider;
An orbiting scroll engaged with the fixed scroll to form a compression chamber with the fixed scroll;
An electric motor for driving the orbiting scroll;
A rotation suppressing member that prevents rotation of the orbiting scroll;
A main bearing supporting the orbiting scroll;
A suction pipe having an opening opening to the low pressure space;
A rectifying plate for diverting the refrigerant drawn into the closed container from the suction pipe;
The fixed scroll, a compression mechanism including the orbiting scroll and the rotation suppressing member, the electric motor, the straightening vane, and the main bearing are disposed in the low pressure space,
The scroll compressor, wherein the fixed scroll and the orbiting scroll are disposed between the partition plate and the main bearing,
In the flow straightening plate, a part of the refrigerant sucked from the suction pipe flows to the compression mechanism side without colliding with the flow straightening plate, and the remaining flow of the refrigerant sucked from the suction pipe is the flow straightening It is configured to collide with a plate and be diverted to the motor side,
Scroll compressor.
The compression mechanism portion has a suction portion to which at least a part of the refrigerant sucked from the suction pipe is sucked,
Assuming that the opening area of the opening is A, and the area of the overlapping portion of the opening of the opening and the straightening vane when viewed from the axial center direction of the suction pipe is B, A> B, and The overlapping portion is located on the suction unit side of the straightening vane,
The scroll compressor according to claim 1.
A hole is provided in the overlapping portion of the straightening vane,
The scroll compressor according to claim 2.
The straightening vanes are provided to cover left and right portions of the opening when viewed from the axial center direction of the suction pipe.
The scroll compressor according to claim 2 or claim 3.
The suction pipe is configured such that at least a part of the opening of the opening overlaps with the suction portion when viewed from the axial center direction of the suction pipe.
The scroll compressor according to any one of claims 2 to 4.
Assuming that the diameter of the opening is d, the distance between the suction pipe and the straightening vane is greater than d / 2 and less than d.
The scroll compressor according to any one of claims 2 to 4.
The area B of the overlapping portion is more than 30% and less than 70% of the opening area A of the opening,
The scroll compressor according to any one of claims 2 to 6.