JP7022902B2 - Scroll compressor - Google Patents

Description

The present disclosure relates to a scroll compressor.

In recent years, a partition plate is provided in a compression vessel, and a compression element having a fixed scroll and a swivel scroll and an electric element for swiveling and driving the swivel scroll are arranged in a chamber on the low pressure side partitioned by the partition plate. Closed scroll compressors are known. In this type of closed 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 a partition plate via the discharge port of the fixed scroll. It is discharged into the chamber on the high pressure side (see, for example, Patent Document 1).

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

However, in the above-mentioned conventional configuration, when the refrigerant is diverted by the rectifying plate 202, the direction of the flow of the refrigerant after colliding with the rectifying plate 202 and being diverted is parallel to the axis of rotation (vertical direction in FIG. 10). Become. Therefore, the refrigerant flowing out from the straightening vane 202 to the opposite side of 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 decreases and the volumetric efficiency decreases.

Japanese Unexamined Patent Publication No. 4-255595

The present disclosure solves the above-mentioned problems, 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 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. However, the straightening vane is configured so as to collide with the straightening vane and be diverted to the motor side.

As a result, the rectifying plate allows the amount of refrigerant required for cooling the motor to flow out to the motor side, while the remaining refrigerant can flow directly to the compression mechanism portion side. Therefore, it is possible to prevent a decrease in the efficiency of the compressor due to the sucked refrigerant being heated by the partition plate.

Cross-sectional view of the scroll compressor according to the first embodiment of the present disclosure cut in the vertical direction. 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. Side view of the swivel scroll of the scroll compressor according to the first embodiment. A cross-sectional view of the swivel scroll in FIG. 2A cut along the XX line of FIG. 2A. Bottom view of the fixed scroll of the scroll compressor according to the first embodiment of the present disclosure. An exploded perspective view of the fixed scroll according to the first embodiment as viewed from diagonally above. A perspective view of the main bearing of the scroll compressor according to the first embodiment as viewed from diagonally above. Top view of the rotation suppressing member of the scroll compressor according to the first embodiment. Sectional drawing of the main part of the scroll compressor which concerns on Embodiment 1 A perspective view showing a cross section of a main part of the scroll compressor according to the first embodiment. Cross-sectional view of the scroll compressor according to the second embodiment of the present disclosure cut in the vertical direction. Cross-sectional view of the scroll compressor according to the second embodiment cut in the vertical direction when viewed from the axis center of the suction pipe. Cross-sectional view of a conventional scroll compressor cut in the vertical direction

The scroll compressor according to one 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 that is meshed with the fixed scroll. It has a swivel scroll that forms a compression chamber, an electric motor that drives the swivel scroll, a rotation suppression member that prevents the swivel scroll from rotating, a main bearing that supports the swivel scroll, and an opening that opens toward a low-pressure space. It has a suction pipe and a rectifying plate that divides the refrigerant sucked into the closed container from the suction pipe. A compression mechanism including a fixed scroll, a swivel scroll and a rotation suppressing member, an electric motor, a straightening vane and a main bearing are arranged in a low pressure space, and a fixed scroll and a swivel scroll are arranged between a partition plate and the main bearing. In the straightening vane, a part of the refrigerant sucked from the suction pipe flows to the compression mechanism side without colliding with the straightening vane, and the rest of the refrigerant sucked from the suction pipe collides with the straightening vane and moves to the motor side. It is configured to be split.

As a result, the rectifying plate allows the amount of refrigerant required for cooling the motor to flow out to the motor side, while the remaining refrigerant can flow directly to the compression mechanism portion side. Therefore, it is possible to prevent a decrease in the efficiency of the compressor due to the sucked refrigerant being heated by the partition plate.

In the scroll compressor according to another aspect of the present disclosure, the compression mechanism portion has a suction portion in which at least a part of the refrigerant sucked from the suction pipe is sucked, and the opening area of the opening of the suction pipe is A. Assuming that the area of the overlap portion between the opening of the opening and the rectifying plate when viewed from the axial center direction of the suction pipe is B, A> B, and the overlapping portion is the compression mechanism portion in the rectifying plate. It may be configured to be located on the suction portion 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 the refrigerant required for cooling the motor is diverted to the motor side, and the remaining refrigerant directly flows out to the suction part side of the compression mechanism part, so that the refrigerant reaches a relatively high temperature partition plate. Is avoided from colliding. Therefore, the sucked refrigerant is directly sucked from the suction part of the fixed scroll without being heated by the partition plate. As a result, it is possible to suppress a decrease in the refrigerant density due to heating of the refrigerant and 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 in a portion of the straightening vane that overlaps with the opening of the opening.

According to this configuration, it is possible to suppress a decrease in the refrigerant density due to heating of the refrigerant and improve the efficiency of the scroll compressor by a simple configuration in which the holes are provided. Therefore, it is not necessary to change the positions of the suction tube and the straightening vane from the conventional scroll compressor.

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

According to this configuration, the refrigerant sucked from the suction pipe is suppressed from being diverted from the opening of the opening in the left-right direction of the opening, that is, in the circumferential direction of the closed container, and the refrigerant is suppressed to the compression mechanism side and the electric motor side. Can be efficiently flowed out, and the refrigerant can be more efficiently guided to the suction portion of the compression mechanism portion. Therefore, it is possible to reduce the contact of the refrigerant with the partition plate, suppress the decrease in the refrigerant density, and improve the efficiency of the scroll compressor.

In the scroll compressor according to another aspect of the present disclosure, the suction pipe has such that at least a part of the opening of the opening overlaps with the suction portion of the compression mechanism portion when viewed from the axial center direction of the suction pipe. It may be configured in.

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

The scroll compressor according to another aspect of the present disclosure may be configured such that the distance between the suction tube and the straightening vane is larger than d / 2 and smaller than d, where d is the diameter of the opening of the suction tube. ..

According to this configuration, the pressure loss of the refrigerant flowing between the straightening vane and the inner wall surface of the closed container can be reduced, so that the effect of the diversion by the straightening vane can be enhanced. 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 rectifying plate 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 and smaller than 70%.

According to this configuration, the refrigerant can be appropriately divided into each of the compressor side and the motor side, and the efficiency of the compression mechanism unit can be improved while efficiently cooling the motor.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. 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 of the scroll compressor according to the first embodiment cut in the vertical direction. Further, FIG. 1B is a cross-sectional view of the scroll compression according to the first embodiment, which is cut in the vertical direction when viewed from the axial center of the suction pipe.

As shown in FIGS. 1A and 1B, the compressor 1 includes a cylindrical closed container 10 long in the vertical direction as an outer shell. In the present specification, the vertical direction is the Z-axis direction (rotational axis direction of the motor) in each figure.

The compressor 1 is a closed scroll compressor including a compression mechanism unit 170 for compressing the refrigerant and an electric motor 80 for driving the compression mechanism unit 170 inside the closed container 10. The compression mechanism unit 170 is composed of at least a fixed scroll 30, a swivel scroll 40, a main bearing 60, and an old dam ring 90 which is a rotation control member.

Above the inside of the closed container 10, a partition plate 20 for vertically partitioning the inside of the closed container 10 is provided. 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 the high-pressure refrigerant after being compressed by the compression mechanism unit 170, and the low-pressure space 12 is a space filled with the low-pressure refrigerant before being compressed by the compression mechanism unit 170. An oil sump 15 in which lubricating oil is stored is formed at the bottom of the low pressure space 12.

The closed container 10 includes a refrigerant suction pipe (hereinafter referred to as a suction pipe) 13 that communicates the outside of the closed container 10 with the low pressure space 12, and a refrigerant discharge pipe 14 that communicates 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 into the low-pressure space 12 from a refrigeration cycle circuit (not shown) provided outside the closed container 10 via a suction pipe 13. Further, the high-pressure refrigerant compressed by the compression mechanism unit 170 is introduced into the high-pressure space 11, and then discharged from the high-pressure space 11 to the refrigeration cycle circuit via the refrigerant discharge pipe 14.

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

[2. Rectifier plate configuration]
A straightening vane 160 is attached to the inner wall surface of the closed container 10 so as to face the inner opening (hereinafter, opening) 13a of the closed container of the suction pipe 13. The upper partition plate 20 side of the straightening vane 160 is closed. That is, the straightening vane 160 is configured so 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 to the compression mechanism 170 side without colliding with the straightening vane 160, and the rest of the refrigerant sucked from the suction pipe 13 is the straightening vane. It is configured to collide with 160 and be split 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, 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 is the suction portion of the compression mechanism portion 170 in the rectifying plate 160 (in the present embodiment, the suction portion 38 of the fixed scroll 30). ) Is provided on the side.

In FIG. 1B, the opening of the opening 13a is a circular region shown by a vertical line. Further, the overlapping portion is a part of the circle shown by both the vertical line and the horizontal line.

Then, in the present embodiment, as shown in FIG. 1B, the straightening vane 160 is configured to cover the left and right portions (ends in the circumferential direction of the closed container 10) of the opening 13a of the suction pipe 13.

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

Further, 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.

Further, the area B of the overlapping portion where the opening of the opening 13a of the suction pipe 13 and the rectifying plate 160 overlap is larger than 30% of the opening area A of the opening 13a of the suction pipe 13 and smaller than 70%. It is configured.

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

The fixed scroll 30 is a non-turning scroll. The fixed scroll 30 is arranged below the partition plate 20 adjacent to the partition plate 20. The swivel scroll 40 is arranged below the fixed scroll 30 so as to be meshed with the fixed scroll 30.

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

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

By engaging the swirl wrap 42 of the swirl scroll 40 and the fixed swirl wrap 32 of the fixed scroll 30, a compression chamber 50 is formed between the swirl scroll 40 and the fixed scroll 30. The compression chamber 50 is formed on the inner wall (described later) side and the outer wall (described later) side of the swirl swirl wrap 42.

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

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

As shown in FIGS. 1A and 1B, the rotation axis 70 has an axis in the vertical direction. 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 sump 15. An eccentric shaft 71 eccentric with respect to the axis of the rotating shaft 70 is provided at the upper end of the rotating shaft 70.

The eccentric shaft 71 is slidably inserted into the lower boss portion 43 via the swing bush 78 and the swivel bearing 79. The lower boss portion 43 is swiveled by the eccentric shaft 71.

An oil passage 72 through which lubricating oil passes is formed inside 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 is opened in the oil sump 15 as a suction port 73 provided at the lower end of the rotating shaft 70. A paddle 74 for pumping lubricating oil from the suction port 73 to the oil passage 72 is provided above the suction port 73.

The rotary shaft 70 is connected to the electric motor 80. The electric motor 80 is arranged between the main bearing 60 and the auxiliary bearing 16. The electric motor 80 includes a stator 81 fixed to the closed container 10 and a rotor 82 arranged inside the stator 81.

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

The rotation shaft 70 rotates in a balanced manner by the centrifugal force generated by the balance weight 17a and the balance weight 17b and the centrifugal force generated by the revolution movement of the swivel scroll 40. The balance weight 17a and the balance weight 17b may be provided on the rotor 82.

An old dam ring 90, which is a rotation suppressing member, is provided between the swivel scroll 40 and the main bearing 60. The old dam ring 90 prevents the turning scroll 40 from rotating. As a result, the turning scroll 40 does not rotate on its axis, but makes a turning motion with respect to the fixed scroll 30.

The fixed scroll 30, the swivel scroll 40, the electric motor 80, the old dam ring 90, and the main bearing 60 are arranged in the low pressure space 12. Further, the fixed scroll 30 and the swivel scroll 40 are arranged 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 either the fixed scroll 30 or the swivel scroll 40. Of the fixed scroll 30 and the swivel scroll 40, at least one of which is provided with an elastic body is provided so as to be movable in the axial direction in at least a part of the section between the partition plate 20 and the main bearing 60. .. The at least a part of the section is, for example, between the partition plate 20 and the swivel scroll 40, or between the fixed scroll 30 and the main bearing 60.

In the present embodiment, the fixed scroll 30 is provided so as to be movable 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 of the columnar member 100 is inserted and fixed in the bearing side hole 102, while the upper end is slidably inserted in the scroll side hole 101.

The columnar member 100 regulates the rotation and radial movement of the fixed scroll 30 and allows the fixed scroll 30 to move in the axial direction. That is, the fixed scroll 30 is supported by the main bearing 60 by the columnar member 100, and is a part of the section between the partition plate 20 and the main bearing 60, more specifically, between the partition plate 20 and the swivel scroll 40. It is provided so as 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 evenly in the circumferential direction.

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

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

When the electric motor 80 is driven, the rotating shaft 70 rotates together with the rotor 82. The swivel scroll 40 swivels around the central axis of the rotary shaft 70 without rotating due to the eccentric shaft 71 and the old dam 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 straightening vane 160 and is separated.

In the present embodiment, as shown in FIG. 1B, the suction pipe 13 and the straightening vane 160 have an area of the opening 13a of the suction pipe 13 as A, 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 between the rectifying plate 160 and the rectifying plate 160 is B, A> B, and the overlapping portion is provided on the suction portion 38 side of the fixed scroll 30 in the rectifying plate 160.

Therefore, the refrigerant introduced from the suction pipe 13 collides with the overlapping portion of the straightening vane 160, a part thereof is diverted to the motor 80 side, and the rest passes through the opening 13a of the suction pipe 13. It flows directly to the compression mechanism portion 170 side. That is, only the amount of the refrigerant required for cooling the motor 80 is diverted to the 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 to the suction section 38 side of the compression mechanism section 170 and is sucked from the suction section 38 while suppressing collision with the partition plate 20 which has become relatively hot. Therefore, it is possible to prevent the refrigerant sucked from the suction pipe 13 from being heated by the partition plate 20 and to suppress a decrease in the refrigerant density due to the heating of the refrigerant. This makes it possible to improve the efficiency of the scroll compressor.

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

As a result, the refrigerant sucked from the suction pipe 13 is suppressed from being diverted from the opening 13a of the suction pipe 13 in the left-right direction, that is, in the circumferential direction of the closed container 10, and the compression mechanism portion 170 side and the motor 80 side are suppressed. Can be efficiently split into. Therefore, the refrigerant is more efficiently guided 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 the refrigerant density can be suppressed, and the efficiency of the scroll compressor can be improved.

Further, in the present embodiment, at least a part of the opening of the opening 13a of the suction pipe 13 is configured to overlap with the suction portion 38 of the fixed scroll 30 when viewed from the axial center direction of the suction pipe. There is.

As a result, the suction refrigerant flowing through the part of the opening 13a of the suction pipe 13 linearly heads toward the suction portion 38 of the compression mechanism portion 170. Therefore, the refrigerant can be directly sucked into the suction unit 38 of the compression mechanism unit 170 more efficiently. Therefore, it is possible to prevent the refrigerant from coming into contact with the partition plate 20, suppress a decrease in the refrigerant density, and improve the efficiency of the scroll compressor.

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 within a range larger than d / 2 and smaller than d.

Since the distance between the suction pipe 13 and the straightening vane 160 is 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 closed container 10) can be reduced. .. Further, since the distance between the suction pipe 13 and the straightening vane 160 is set to be smaller than d, the sucked refrigerant is easily separated to the motor 80 side 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 closed container 10 can be reduced, the refrigerant is efficiently divided into the motor 80 side and the compression mechanism portion 170 side. Therefore, the efficiency of the scroll compressor can be improved.

Further, in the present embodiment, the area B of the overlapping portion between the opening 13a of the suction pipe 13 and the straightening vane 160 is within a range larger than 30% and smaller than 70% of the opening area A of the opening 13a of the suction pipe 13. Is.

By making the area B of the overlapping portion larger than 30% of the opening area A of the opening 13a of the refrigerant suction pipe 13, it is possible to secure an appropriate amount of the refrigerant to be diverted to the motor 80 side. It is possible to cool the electric motor 80 satisfactorily.

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

That is, it is possible to satisfactorily cool the electric motor 80 and also satisfactorily compress the refrigerant by the compression mechanism unit 170. Then, the refrigerant sucked from the suction pipe 13 is directly sucked from the suction unit 38 of the compression mechanism unit 170 without colliding with the relatively high temperature partition plate 20 and being heated, so that the compression mechanism unit The compression efficiency of the refrigerant in 170 can be improved.

Then, 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 sump 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 to the bearing portion 61, the auxiliary bearing 16 and the boss accommodating portion 62 from the first lubrication port 75, the second lubrication port 76, and the third lubrication port 77, respectively. Further, the lubricating oil pumped up to the boss accommodating portion 62 is guided to the sliding surface between the main bearing 60 and the swivel scroll 40, is discharged through the return path 63 (see FIG. 5), and returns to the oil sump 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 swivel scroll of the scroll compressor according to the present embodiment. FIG. 2B is a cross-sectional view of the swivel scroll in FIG. 2A cut along the line XX of FIG. 2A.

The swirl swirl wrap 42 shown in FIG. 2A has an involute curved cross section starting from the start end 42a located on the center side of the swirl scroll end plate 41 and gradually expanding its radius toward the end end 42b located on the outer peripheral side. (See FIG. 2B). The swirl swirl wrap 42 has a predetermined height (length in the vertical direction) and a predetermined wall thickness (length in the radial direction of the swirl swirl wrap 42).

A pair of first key grooves 91, which are long in the direction from the outer peripheral side to the central side, are provided at both ends of the lower surface of the swivel scroll end plate 41 (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 from diagonally above.

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

The fixed spiral wrap 32 includes an inner wall (wall surface on the center side) and an outer wall (wall surface on the outer peripheral side) from the start end 32a to the intermediate portion 32b, and includes only an inner wall from the intermediate portion 32b to the end 32c.

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

The bypass port 36 is a set of three small holes on the bypass port 36 communicating with the compression chamber 50 formed on the outer wall side of the swirl swirl wrap 42 (see FIG. 2B) and on the inner wall side of the swirl swirl wrap 42. Two sets of bypass ports 36 communicating with the formed compression chamber 50 are provided. The medium pressure port 37 is arranged in the vicinity of the intermediate portion 32b in a region where the intermediate pressure refrigerant during compression exists.

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

Each of the pair of first flanges 34a is arranged substantially evenly in the circumferential direction of the rotation shaft 70 with a predetermined interval. Further, each of the pair of second flanges 34b is arranged substantially evenly in the circumferential direction of the rotation shaft 70 with 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 a scroll side hole 101 into which the upper end of the columnar member 100 (see FIG. 1) is inserted. One scroll side hole 101 is provided on each of the pair of first flanges 34a. The two scroll-side hole portions 101 are arranged at predetermined intervals in the circumferential direction. Desirably, the two scroll side holes 101 are evenly arranged in the circumferential direction. The scroll side hole 101 may not be a through hole, but may be a recess recessed from the lower surface side.

The scroll side hole 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 keyway 92 (see FIG. 3). The second key groove 92 is a pair of grooves provided on each of the pair of second flanges 34b and long in the direction from the outer peripheral side to the center side.

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

Further, on the upper surface of the fixed scroll 30, a ring-shaped convex portion 310 is provided on the outer peripheral side of the upper boss portion 39. A concave portion is formed on the upper surface of the fixed scroll 30 by the upper boss portion 39 and the ring-shaped convex portion 310. This recess forms a medium 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 hole diameter of the medium pressure port 37 is smaller than the wall thickness of the swirl swirl wrap 42. This prevents communication between the compression chamber 50 formed on the inner wall side of the swirl swirl wrap 42 and the compression chamber 50 formed on the outer wall side of the swirl swirl wrap 42.

On the upper surface of the upper boss portion 39, a bypass check valve 121 that can open and close the bypass port 36 and a bypass check valve stop 122 that prevents excessive deformation of the bypass check valve 121 are provided. By using a reed valve as the bypass check valve 121, the height can be reduced. Further, by using a V-shaped reed valve as the bypass check valve 121, the bypass port 36 communicating with the compression chamber 50 formed on the outer wall side of the swirl swirl wrap 42 and the inner wall side of the swirl swirl wrap 42. The bypass port 36 communicating with the compression chamber 50 formed in the above can be opened and closed by one reed valve.

On the upper surface (bottom surface of the recess) of the fixed scroll 30, there is a medium pressure check valve (not shown) that can open and close the medium pressure port 37, and a medium pressure check valve that prevents excessive deformation of the medium pressure check valve. A valve stop (not shown) is provided. By using a reed valve as a medium pressure check valve, the size in the height direction can be made compact. 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 from diagonally above.

As shown in FIG. 5, the outer peripheral portion of the main bearing 60 is provided with a bearing side hole 102 into which the lower end of the columnar member 100 (see FIG. 1) is inserted. Two bearing side hole portions 102 are provided at predetermined intervals in the circumferential direction. Desirably, the two bearing side holes 102 are evenly arranged in 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. One end of the return path 63 may be opened on the upper surface of the main bearing 60. Further, the other end of the return path 63 may be opened on the side surface of the main bearing 60.

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

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

As shown in FIG. 6, the Oldham ring 90 includes a ring portion 95 having a substantially annular shape, 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 so 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 keyway 91 (see FIG. 2B) of the swivel scroll 40, and the second key 94 with the second keyway 92 (see FIG. 3) of the fixed scroll 30. Engage. As a result, the turning scroll 40 can make a turning motion with respect to the fixed scroll 30 without rotating.

In the present embodiment, the fixed scroll 30, the swivel scroll 40, and the old dam ring 90 are arranged in this order from above in the axial direction of the rotating shaft 70 (see FIG. 1). Therefore, the first key 93 and the second key 94 are formed on the same plane in the ring portion 95. As a result, when the old dam ring 90 is produced, the first key 93 and the second key 94 can be machined from the same direction, and the number of times the old dam ring 90 is detached from the machining device can be reduced. Therefore, it is possible to improve the processing accuracy of the old dam ring 90 and reduce the processing cost.

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

As shown in FIG. 7, a second discharge port 21 is provided at the center of the partition plate 20. On the upper surface of the partition plate 20, a discharge check valve 131 that can open and close the second discharge port 21 and a discharge check valve stop 132 that prevents excessive deformation of the discharge check valve 131 are provided. ..

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, back pressure is applied to the upper surface side of the fixed scroll 30. That is, when the high pressure is applied to the discharge space 30H, the fixed scroll 30 is pressed against the swivel scroll 40. Therefore, the gap between the fixed scroll 30 and the swivel scroll 40 can be eliminated, and the compressor 1 performs highly efficient operation.

The plate thickness of the discharge check valve 131 is larger than the plate thickness of the bypass check valve 121. This makes it possible to prevent the discharge check valve 131 from opening before the bypass check valve 121.

The volume of the second discharge port 21 is larger than the volume of the first discharge port 35. This makes it possible to reduce the pressure loss of the refrigerant discharged from the compression chamber 50.

Further, a taper may be formed on the inflow side of the second discharge port 21. As a result, the pressure loss can be further reduced.

On the lower surface of the partition plate 20, a projecting portion 22 projecting in an annular shape 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 protruding portion 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 portion 39. That is, the first seal member 141 is arranged between the partition plate 20 and the fixed scroll 30 in a gap located 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 arranged outside the first seal member 141. The tip of the second seal member 142 is in contact with the inner surface of the ring-shaped convex portion 310. That is, the second seal member 142 is arranged between the partition plate 20 and the fixed scroll 30 in a gap located on the outer periphery of the medium pressure space 30M.

In other words, the first seal member 141 and the second seal member 142 form a discharge space 30H and a medium pressure space 30M between the partition plate 20 and the fixed scroll 30. 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 separates the discharge space 30H and the medium pressure space 30M, and the second seal member 142 is a seal member that separates 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 fluororesin, is suitable in terms of sealability and assembling property. Further, as the first seal member 141 and the second seal member 142, those obtained by mixing a fiber material with a fluororesin are used, so that the reliability of the seal is improved.

The first seal member 141 and the second seal member 142 are sandwiched between the closing member 150 and the projecting portion 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 arranged in the closed 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 has a ring-shaped portion 151 arranged so as 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 the inner peripheral side portion of the upper surface of the ring-shaped portion 151 and the lower surface of the protruding portion 22. Further, the inner peripheral side of the second seal member 142 is sandwiched between the outer peripheral side portion of the upper surface of the ring-shaped portion 151 and the lower surface of the protruding portion 22.

That is, the ring-shaped portion 151 faces 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 protrusions 22. The upper end of the protruding portion 152 is crimped so that the ring-shaped portion 151 is pressed against the lower surface of the protruding portion 22. That is, the closing member 150 is fixed to the partition plate 20 so that the ring-shaped portion 151 is pressed against the lower surface of the protruding portion 22 by deforming the upper end of the protruding 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 side of the partition plate 20, and is the first. 2 The outer peripheral portion of the seal member 142 projects 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 closed container 10, so that the inner peripheral side portion of the first seal member 141 is formed by the fixed scroll 30. It is pressed against the outer peripheral surface of the upper boss portion 39, and the outer peripheral side portion 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.

The medium pressure space 30M communicates with the region in the compression chamber 50 where the intermediate pressure refrigerant during compression exists by the medium pressure port 37. Therefore, the pressure in the medium pressure space 30M is lower than the pressure in the discharge space 30H and higher than the pressure in the low pressure space 12.

In this way, by forming the medium pressure space 30M in addition to the discharge space 30H between the partition plate 20 and the fixed scroll 30, it is easy to adjust the pressing force of the fixed scroll 30 against the swivel scroll 40. 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 the refrigerant can be reduced.

(Embodiment 2)
FIG. 9A is a cross-sectional view of the scroll compressor according to the present embodiment cut in the vertical direction. Further, 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 suction pipe 13 opening 13a and the straightening vane 160 in the straightening vane 160 when viewed from the axial center direction of the suction pipe 13. 160a is provided.

Since other configurations are the same as those of the compressor 1 according to the first embodiment shown in FIG. 1, the same configurations as those described with reference to FIG. 1 are designated by the same reference numerals and the description thereof will be omitted.

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

Therefore, if the size of the hole portion 160a is such that the relationship between the opening area A and the area B of the overlapping portion described in the first embodiment is satisfied, 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 is not changed, for example, by shifting it up and down, and a hole is added to the configuration of the existing compressor. Similarly, it is possible to suppress a decrease in the refrigerant density and improve the efficiency of the compressor.

As described above, the present disclosure can prevent a decrease in compression efficiency due to heating of the refrigerant sucked in the partition plate while ensuring the cooling performance for the motor. Therefore, it is possible to provide a highly efficient scroll compressor. Therefore, it can be widely applied as a compressor for refrigerating cycle devices such as water heaters, hot water heating devices, and air conditioners.

1 Compressor 10 Closed container 11 High pressure space 12 Low pressure space 13 Refrigerant suction pipe (suction pipe)
13a Closed container inner opening (opening)
14 Refrigerant discharge pipe (discharge pipe)
16 Sub-bearing 17a Balance weight 17b Balance weight 20 Partition plate 21 Second discharge port 22 Protruding part 30 Fixed scroll 30H Discharge space 30M Medium pressure space 31 Fixed scroll end plate 32 Fixed spiral wrap 32a Starting end 32b Intermediate part 32c Termination end 33 Peripheral wall 34a 34b Flange 35 1st discharge port 36 Bypass port 37 Medium pressure port 38 Suction part 39 Upper boss part 40 Swivel scroll 42 Swirl swirl wrap 42a Start end 42b Termination 43 Lower boss part 50 Compression chamber 60 Main bearing 61 Bearing part 62 Boss accommodating part 63 Return route 70 Rotating shaft 71 Eccentric shaft 72 Oil passage 73 Suction port 74 Paddle 75 Refueling port 76 Refueling port 77 Refueling port 80 Motor motor 81 Stator 82 Rotor 90 Rotation suppression member (Oldam 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 Seal member 150 Closure member 151 Ring-shaped part 152 Protruding part 160 Check valve 160a Hole part 170 Compression mechanism part 221 Hole part

Claims (5)

With a closed container
A partition plate that divides the inside of the closed container into a high-pressure space and a low-pressure space,
With the fixed scroll adjacent to the partition plate,
A swivel scroll that is meshed with the fixed scroll to form a compression chamber together with the fixed scroll.
The motor that drives the turning scroll and
The rotation suppressing member that prevents the rotation of the turning scroll and the rotation suppressing member
The main bearing that supports the swivel scroll and
A suction tube having an opening that opens toward the low pressure space,
It has a rectifying plate that separates the refrigerant sucked from the suction pipe into the closed container.
The fixed scroll, the compression mechanism including the swivel scroll and the rotation suppressing member, the motor, the straightening vane, and the main bearing are arranged in the low pressure space.
A scroll compressor in which the fixed scroll and the swivel scroll are arranged between the partition plate and the main bearing.
In the rectifying plate, a part of the refrigerant sucked from the suction pipe flows to the compression mechanism side without colliding with the rectifying plate, and the rest of the refrigerant sucked from the suction pipe is the rectifying plate. It is configured to collide with the plate and be split to the motor side .
The compression mechanism portion has a suction portion in 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 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 above. The overlapping portion is located on the suction portion side of the straightening vane, and is located on the suction portion side.
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.
Scroll compressor.
A hole is provided in the overlapping portion of the straightening vane.
The scroll compressor according to claim 1 .
The straightening vane is provided so as to cover the 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 .
Assuming that the diameter of the opening is d, the distance between the suction tube and the straightening vane is larger than d / 2 and smaller than d.
The scroll compressor according to claim 2 or 3 .
The area B of the overlapping portion is larger than 30% and smaller than 70% of the opening area A of the opening.
The scroll compressor according to any one of claims 2 to 4 .

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