WO2016139796A1

WO2016139796A1 - Compressor

Info

Publication number: WO2016139796A1
Application number: PCT/JP2015/056498
Authority: WO
Inventors: 祐一朗今川; 寿史柬理; 宏樹長澤; 貴也木本; 勝巳遠藤
Original assignee: 三菱電機株式会社
Priority date: 2015-03-05
Filing date: 2015-03-05
Publication date: 2016-09-09
Also published as: CN105937496A; CN205503461U

Abstract

A compressor 100 comprises: a compression mechanism part 3 that includes a compression chamber 14 that compresses a fluid and a discharge port 16 that discharges the fluid compressed by the compression chamber 14; and a reed valve 17 that includes a fixed part 17a that is fixed to the compression mechanism part 3 and a movable part 17b that opens/closes the discharge port 16, the reed valve being provided outside the compression chamber 14. A groove 20 is formed in the compression mechanism part 3, the groove 20 accommodating at least part of the reed valve 17. The groove 20 includes a port periphery section 20a that surrounds the discharge port 16 and a reinforcement section 23 that surrounds the port periphery section 20a. The thickness of a part of the compression mechanism part 3 where the reinforcement section 23 is formed gradually increases toward the outside from the port periphery section 20a.

Description

Compressor

The present invention relates to a compressor with improved compression efficiency and reliability.

Conventionally, there is known a compressor in which the thickness of the discharge port for discharging the refrigerant is reduced to improve the compression efficiency. For example, in the conventional compressor described in Patent Document 1 below, a reinforcing portion having a thickness larger than the thickness of the valve seat portion is formed in a part of the circumferential direction outside the valve seat portion, The thin valve seat part and the part around the valve seat part are reinforced.

JP 2000-87893 A

However, since the conventional compressor described in Patent Document 1 has a configuration in which the reinforcing portion is formed only in a part in the circumferential direction, the reinforcement around the port surrounding the discharge port is insufficient. Therefore, in the compressor of patent document 1, the thickness of the port peripheral part surrounding a discharge port is thick, and the compression efficiency of a compressor is bad.

Furthermore, in the conventional compressor described in Patent Document 1, since the fluid easily flows along the circumferential direction of the valve seat portion to the portion other than the reinforcement portion, it is arranged above the discharge port. When the provided reed valve opens and closes, a torsional force may act on the reed valve. Since the force in the twisting direction acts on the reed valve, the reed valve may be deformed or damaged. Therefore, the compressor described in Patent Document 1 has poor reliability.

The present invention has been made against the background of the above problems, and an object thereof is to obtain a compressor with improved compression efficiency and reliability.

A compressor according to the present invention includes a compression chamber that compresses a fluid, a discharge port that discharges the fluid compressed in the compression chamber, a fixed portion that is fixed to the compression mechanism portion, and a discharge port. A reed valve that is disposed outside the compression chamber, and the compression mechanism has a groove that accommodates at least a portion of the reed valve. The thickness of the portion of the compression mechanism portion where the reinforcing portion is formed gradually increases from the port peripheral portion toward the outside, including a port peripheral portion surrounding the discharge port and a reinforcing portion surrounding the port peripheral portion. It ’s thick.

According to the present invention, a compressor with improved compression efficiency and reliability can be obtained.

It is the figure which described typically an example of the longitudinal cross-section of the compressor which concerns on Embodiment 1 of this invention. It is the figure which described typically an example of the cross section of the 1st compression mechanism part described in FIG. It is the figure which described typically the longitudinal cross-section which expanded the part of the discharge port of FIG. It is the figure which described typically the upper surface of the upper bearing described in FIG. FIG. 5 is a diagram schematically showing a groove portion of the AA cross section of FIG. 4. FIG. 5 is a diagram schematically showing a recessed portion of the BB cross section of FIG. 4. It is the figure which described typically the comparative example 1 of FIG. FIG. 8 is a diagram schematically showing a groove portion of a CC cross section in FIG. 7.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof is omitted or simplified as appropriate. In addition, the shape, size, arrangement, and the like of the configuration described in each drawing can be changed as appropriate within the scope of the present invention.

Embodiment 1 FIG.
[Compressor]
FIG. 1 is a diagram schematically illustrating an example of a longitudinal section of a compressor according to Embodiment 1 of the present invention. A compressor 100 illustrated in FIG. 1 compresses a fluid such as a refrigerant gas. In the following description, the compressor 100 that compresses the refrigerant gas will be described. The compressor 100 compresses the low-pressure refrigerant gas sucked from the suction pipe 25 and discharges the compressed high-pressure refrigerant gas from the discharge pipe 26 to the outside of the sealed container 1. The compressor 100 includes an electric motor unit 2 and a compression unit 30 that are accommodated in the sealed container 1. The compressor 100 is not limited to the hermetic compressor as shown in FIG. 1, and may be an open compressor in which the electric motor unit 2 is disposed outside the hermetic container 1. .

The electric motor unit 2 transmits power to the compression unit 30 via the rotary shaft 4, and includes a stator 2a and a rotor 2b. The compression part 30 receives power from the electric motor part 2 and compresses the refrigerant gas in the compression chamber 14, and includes the cylinder part 7, the upper bearing 12, the lower bearing 13, and the rolling piston 9. The compression unit 30 according to this embodiment includes a first compression mechanism unit 3a and a second compression mechanism unit 3b stacked with the partition plate 5 interposed therebetween. The compressor 100 according to this embodiment may include any one of the first compression mechanism unit 3a and the second compression mechanism unit 3b. The first compression mechanism section 3a compresses the refrigerant gas sucked into the first compression chamber 14a inside the first cylinder section 7a, and is driven by receiving power from the electric motor section 2 and is a first rolling piston. 9a is included. The second compression mechanism portion 3b compresses the refrigerant gas sucked into the second compression chamber 14b inside the second cylinder portion 7b, and is driven by receiving power from the electric motor portion 2. A rolling piston 9b is included. In addition, since the 1st compression mechanism part 3a and the 2nd compression mechanism part 3b are the same structures, in order to make an understanding of this embodiment easy in the following description, only about the 1st compression mechanism part 3a. And the description of the second compression mechanism 3b is omitted.

Next, the configuration of the first compression mechanism unit 3a will be described with reference to FIGS. FIG. 2 is a diagram schematically illustrating an example of a cross section of the first compression mechanism section illustrated in FIG. 1, and FIG. 3 is a schematic diagram illustrating an enlarged vertical section of the discharge port portion of FIG. 1. FIG. As shown in FIG. 2, the 1st compression mechanism part 3a is provided with the 1st rolling piston 9a and the vane 11 in the 1st compression chamber 14a inside the 1st cylinder part 7a. The first rolling piston 9a is attached to the eccentric shaft portion 8 of the rotating shaft 4, and the power from the electric motor portion 2 is transmitted to the first rolling piston 9a. For example, the eccentric shaft portion 8 is formed of a member different from the rotation shaft 4 and is attached to the rotation shaft 4. In addition, the eccentric shaft part 8 and the rotating shaft 4 may be integrally comprised by the same member. A vane groove 10 and a suction port 15 are formed in the first cylinder portion 7a. The vane 11 is movably held in the vane groove 10 and divides the first compression chamber 14a into a chamber communicating with the suction port 15 and a chamber communicating with the discharge port 16 shown in FIG. It is.

As shown in FIG. 3, the upper bearing 12 attached to the first cylinder portion 7a is formed with a discharge port 16 for discharging the high-pressure refrigerant gas compressed in the first compression chamber 14a. Further, a groove portion 20 that accommodates at least a part of the reed valve 17 is formed on the outer surface of the first compression chamber 14 a of the upper bearing 12. The reed valve 17 is a sheet-like member that operates to open and close the discharge port 16 to prevent the backflow of the refrigerant gas. When the pressure inside the first compression chamber 14a is lower than the pressure inside the sealed container 1, the reed valve 17 closes the discharge port 16 so that the pressure inside the first compression chamber 14a is sealed. When the pressure inside the container 1 is higher, the discharge port 16 is operated to be opened. The reed valve 17 has a fixed portion 17 a fixed to the upper bearing 12 and a movable portion 17 b that opens and closes the discharge port 16. The movable portion 17b of the reed valve 17 may include a protruding portion (not shown) that protrudes toward the discharge port 16 and contacts the peripheral portion of the discharge port 16. Above the reed valve 17, a reed valve pressing member 18 that restricts the range in which the reed valve 17 moves is disposed. The reed valve 17 and the reed valve pressing member 18 are fixed to the upper bearing 12 with a fixing member 19 such as a bolt, for example.

Next, an example of the operation of the compressor 100 configured as described above will be described. When the electric motor unit 2 shown in FIG. 1 is driven, a rotational force is transmitted to the rotary shaft 4. As shown in FIG. 2, the rotational force transmitted to the rotating shaft 4 is transmitted to the eccentric shaft portion 8 attached to the rotating shaft 4, and the first rolling piston 9a attached to the eccentric shaft portion 8 is subjected to the first compression. It rotates inside the chamber 14a. The low-pressure refrigerant gas sucked into the first compression chamber 14a from the suction port 15 is compressed by gradually reducing the volume of the first compression chamber 14a as the first rolling piston 9a rotates. The compressed high-pressure refrigerant gas is discharged from the discharge port 16 of the upper bearing 12 shown in FIG.

4 is a diagram schematically showing the upper surface of the upper bearing shown in FIG. 1, and FIG. 5 is a diagram schematically showing the groove portion of the AA cross section of FIG. FIG. 5 is a diagram schematically showing a recess portion of the BB cross section of FIG. As shown in FIG. 4, a groove portion 20 and a recess portion 22 communicating with the groove portion 20 are formed on the upper surface, which is the outer surface of the first compression chamber 14 a of the upper bearing 12.

As shown in FIGS. 4 and 5, the groove portion 20 includes a valve seat portion 21, a port peripheral portion 20a surrounding the valve seat portion 21, and a reinforcing portion 23 surrounding the port peripheral portion 20a. The valve seat portion 21 is a portion that contacts the reed valve 17 when the reed valve 17 is closed. The thickness of the portion of the upper bearing 12 where the valve seat portion 21 is formed is slightly thicker than the thickness of the portion around the valve seat portion 21 where the port peripheral portion 20a is formed. The valve seat portion 21 slightly protrudes from the port peripheral portion 20a toward the reed valve 17 side. The thickness of the portion of the upper bearing 12 where the reinforcing portion 23 is formed gradually increases from the port peripheral portion 20a toward the outside. The port peripheral portion 20a and the reinforcing portion 23 are formed so that the reed valve 17 does not contact the wall portion of the groove portion 20 including the reinforcing portion 23 when the reed valve 17 opens and closes. When the reinforcing portion 23 is formed to have an inclined surface that is inclined outward from the port peripheral portion 20 a as shown in FIG. 5, the reed valve 17 contacts the wall portion of the groove portion 20. However, since the area of the port peripheral portion 20a can be reduced, the thickness of the portion of the upper bearing 12 where the port peripheral portion 20a and the valve seat portion 21 are formed can be reduced. Further, when the reinforcing portion 23 has an inclined surface that is inclined outward from the port peripheral portion 20a, the refrigerant gas discharged from the discharge port 16 flows smoothly along the inclined surface of the reinforcing portion 23. Therefore, pressure loss is reduced.

As shown in FIGS. 3, 4, and 6, the recessed portion 22 communicates with the groove portion 20 on the side of the groove portion 20 facing the tip portion on the movable portion 17 b side of the reed valve 17. The recess portion 22 is formed deeper than the wall portions on both sides of the reed valve 17 of the groove portion 20, and the refrigerant gas discharged from the discharge port 16 is easily discharged from the front end side of the reed valve 17. Yes. In addition, the hollow part 22 may be connected with the reinforcing part 23 of the groove part 20. Further, the thickness of the portion of the upper bearing 12 where the recess 22 is formed is thicker than the thickness of the portion where the port peripheral portion 20a is formed. The possibility that the portion in which the portion 22 is formed and the portion in which the groove portion 20 continuous with the recessed portion 22 is formed is deformed is reduced. As a result, the thickness of the portion of the upper bearing 12 where the port peripheral portion 20a and the valve seat portion 21 are formed can be reduced.

Further, as shown in FIGS. 4 and 6, a dent reinforcing portion 24 is formed at an edge other than a portion communicating with the groove portion 20 of the dent portion 22. The thickness of the portion of the upper bearing 12 where the recess reinforcing portion 24 is formed is gradually increased outward, and the recess 22 and the portion of the groove 20 formed continuously with the recess 22 are formed. Deformation is suppressed. As a result, the thickness of the portion of the upper bearing 12 where the port peripheral portion 20a and the valve seat portion 21 are formed can be reduced. In addition, as shown in FIG. 7, when the hollow reinforcement part 24 is formed so that it may have an inclined surface inclined outward, the refrigerant gas discharged from the discharge port 16 is made into the hollow reinforcement part 24. Since it flows smoothly through the inclined surface, pressure loss is reduced.

As described above, in this embodiment, as shown in FIG. 4, the groove portion 20 that accommodates at least a part of the reed valve 17 is formed around the discharge port 16 of the upper bearing 12. The groove portion 20 includes a port peripheral portion 20a surrounding the discharge port 16 and a reinforcing portion 23 surrounding the port peripheral portion 20a. As shown in FIG. 5, the reinforcing portion 23 of the upper bearing 12 is formed. The thickness of the portion gradually increases from the port peripheral portion 20a toward the outside. Therefore, in this embodiment, the thickness of the portion of the upper bearing 12 where the discharge port 16 is formed can be reduced. As a result, according to this embodiment, when the refrigerant compressed in the first compression chamber 14a is discharged from the discharge port 16, the amount of high-pressure refrigerant gas remaining in the discharge port 16 can be reduced. The compression efficiency of the compressor 100 can be improved.
For example, FIG. 7 is a diagram schematically illustrating Comparative Example 1 of FIG. 4, and FIG. 8 is a diagram schematically illustrating a groove portion of the CC cross section of FIG. As shown in FIGS. 7 and 8, in Comparative Example 1, unlike the embodiment described in FIGS. 4, 5, etc., the reinforcing portion is not formed in the groove portion 200 of the upper bearing 120. Therefore, in Comparative Example 1, when the thickness of the portion where the valve seat portion 210 and the port peripheral portion 200a of the upper bearing 120 are simply reduced, the port peripheral portion 200a is deformed. Gas leakage may occur, and the upper bearing 120 may be damaged. Therefore, in Comparative Example 1, the thickness of the portion where the valve seat portion 210 and the port peripheral portion 200a are formed must be increased.
Compared with the comparative example 1, in the example of this embodiment, as shown in FIGS. 4 and 5 and the like, the reinforcing portion 23 is formed around the port peripheral portion 20a of the groove portion 20, and therefore the upper bearing 12 The thickness of the portion where the discharge port 16 is formed can be reduced. As a result, according to this embodiment, the compressor 100 with improved compression efficiency can be obtained.

Further, according to this embodiment, the port peripheral portion 20a surrounding the discharge port 16 is formed around the discharge port 16, and the reinforcing portion 23 surrounding the port peripheral portion 20a is formed around the port peripheral portion 20a. ing. Therefore, according to this embodiment, since the refrigerant gas discharged from the discharge port 16 is discharged uniformly from the periphery of the discharge port 16, a force in the twist direction acts when the reed valve 17 is opened and closed. The risk of doing so has been reduced. Therefore, according to this embodiment, the risk of the reed valve 17 being deformed or damaged by the force in the torsional direction acting on the reed valve 17 is reduced, so that the reliability of the compressor 100 is improved. Yes.

Further, in this embodiment, as shown in FIGS. 3, 4, and 6, a recess 22 that communicates with the groove 20 is formed. The hollow portion 22 is a portion including the portion of the groove portion 20 that faces the tip of the reed valve 17 on the movable portion 17b side, and communicates with the groove portion 20, and the refrigerant gas discharged from the discharge port 16 17 easily flows out from the tip end side. As a result, according to this embodiment, when the reed valve 17 is in the open state, the tip side of the reed valve 17 bends smoothly, so that the possibility that a force in the twisting direction acts on the reed valve 17 is reduced. Yes. Furthermore, according to this embodiment, since the tip of the reed valve 17 is bent smoothly, the pressure loss is reduced, and the possibility that the reed valve 17 is deformed or broken is also reduced.

The present invention is not limited to the above embodiment, and can be variously modified within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Further, the configuration requirements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.

For example, in the above-described embodiment, an example in which the protruding ports are formed in the upper bearing 12 and the lower bearing 13 has been described. However, the protruding ports are, for example, other compression mechanisms 3 such as the cylinder unit 7. You may form in the part. In that case, a groove portion for accommodating at least a part of the reed valve may be formed around the portion where the discharge port of the compression mechanism portion 3 is formed, and a recess portion communicating with the groove portion may be formed.

1 sealed container, 2 motor section, 2a stator, 2b rotor, 3 compression mechanism section, 3a first compression mechanism section, 3b second compression mechanism section, 4 rotation shaft, 5 partition plate, 7 cylinder section, 7a 1st Cylinder part, 7b second cylinder part, 8 eccentric shaft part, 9 rolling piston, 9a first rolling piston, 9b second rolling piston, 10 vane groove, 11 vane, 12 upper bearing, 13 lower bearing, 14 compression chamber, 14a 1st compression chamber, 14b 2nd compression chamber, 15 intake port, 16 discharge port, 17 reed valve, 17a fixed part, 17b movable part, 18 reed valve pressing member, 19 fixed member, 20 groove part, 20a port peripheral part, 21 Valve seat part, 22 depression part, 23 reinforcement part, 24 depression reinforcement part, 25 suction pipe, 26 discharge pipe 30 compression unit, 100 compressor, 120 upper bearing, 200 groove, 200a port perimeter, 210 valve seat.

Claims

A compression mechanism having a compression chamber for compressing fluid, and a discharge port for discharging the fluid compressed in the compression chamber;
A reed valve having a fixed part fixed to the compression mechanism part and a movable part for opening and closing the discharge port, and disposed outside the compression chamber;
The compression mechanism portion is formed with a groove portion that accommodates at least a part of the reed valve,
The groove portion includes a port peripheral portion surrounding the discharge port, and a reinforcing portion surrounding the port peripheral portion,
The thickness of the compression mechanism portion where the reinforcing portion is formed gradually increases from the port peripheral portion toward the outside.
Compressor.
The reinforcing portion has an inclined surface inclined outward from the port peripheral portion,
The compressor according to claim 1.
The compression mechanism part is further formed with a hollow part communicating with the groove part outside the compression chamber,
The indented portion communicates with a portion of the groove portion facing the tip of the reed valve on the movable portion side,
The compressor according to claim 1 or 2.
The thickness of the compression mechanism portion where the recess portion is formed is thicker than the thickness of the portion where the port peripheral portion is formed,
The compressor according to claim 3.
A dent reinforcing portion is formed on an edge of a portion different from the portion communicating with the groove portion of the dent portion,
The thickness of the portion of the compression mechanism portion where the dent reinforcing portion is formed is gradually increased outward.
The compressor according to claim 3 or 4.
The hollow reinforcing portion has an inclined surface inclined outward.
The compressor according to claim 5.