Patent Application
20190316589
The present invention relates to a compressor.
A compressor is used in a refrigerant circuit such as an air conditioner. The compressor sucks a low-pressure gas refrigerant into its compression chamber and compresses the low-pressure gas refrigerant to produce a high-pressure gas refrigerant to discharge. Some compressors implement a technique called gas injection in order to improve the capacity of the refrigerant circuit. In the gas injection technique, a pipe called an injection pipe is connected to the compression chamber of the compressor. In a part of the refrigerant circuit, there exists an intermediate pressure gas refrigerant that indicates a pressure value between the low-pressure gas refrigerant and the high-pressure gas refrigerant. The injection pipe introduces the intermediate gas refrigerant into the compression chamber.
The injection pipe often vibrates under pressure pulsation of the gas refrigerant. For this reason, noise is generated or excessive stress may be applied to the injection pipe. In order to reduce problems caused by such vibrations and stress, Patent Document 1 (Japanese Laid-Open Patent Application Publication No. 2010-185406) discloses an air conditioner in which a muffler is attached to the injection pipe.
Due to the weight of the muffler, piping such as the injection pipe connecting the compressor and the muffler receives a large stress, which may cause a problem in terms of reliability of the equipment.
The present invention has been made to accomplish an objective of decreasing defects caused by vibrations and stress that a pipe receives in a compressor.
A compressor according to a first aspect of the present invention compresses a low-pressure refrigerant sucked therein to discharge a high-pressure refrigerant. The compressor includes a first throttle portion, an enlarged flow path portion, a second throttle portion, and a compression element. The first throttle portion receives a refrigerant at an intermediate pressure from an injection pipe of a refrigerant circuit. The enlarged flow path portion receives the refrigerant from the first throttle portion. The second throttle portion receives the refrigerant from the enlarged flow path portion. The compression element has a compression chamber that receives the refrigerant from the second throttle portion. The first throttle portion has a flow path cross-sectional area that is narrower than both a flow path cross-sectional area of the injection pipe and a flow path cross-sectional area of the enlarged flow path portion. The second throttle portion has a flow path cross-sectional area that is narrower than the flow path cross-sectional area of the enlarged flow path portion.
According to this configuration, the first throttle portion, the enlarged flow path portion, and the second throttle portion have different flow path cross-sectional areas. Therefore, the path composed of the first throttle portion, the enlarged flow path portion, and the second throttle portion functions as a muffler and reduces the vibrations of each portion caused by pressure pulsation of the refrigerant.
A compressor according to a second aspect of the present invention is the compressor according to the first aspect of the present invention further including a pressure vessel that accommodates the compression element. At least a part of the second throttle portion is provided in the pressure vessel.
According to this configuration, at least a part of the second throttle portion is provided in the pressure vessel. Since a part of the flow of the pulsating refrigerant passes through the pressure vessel, the noise outside the pressure vessel is reduced as a result.
A compressor according to a third aspect of the present invention is the compressor according to the second aspect of the present invention, wherein at least a part of the enlarged flow path portion is provided in the pressure vessel.
According to this configuration, at least a part of the enlarged flow path portion is provided in the pressure vessel. Therefore, a pressure fluctuation of the refrigerant flowing from the enlarged flow path portion to the second throttle portion occurs in the pressure vessel, whereby the noise outside the pressure vessel is reduced.
A compressor according to a fourth aspect of the present invention is the compressor according to any one of the first aspect to the third aspect of the present invention, wherein the enlarged flow path portion and the second throttle portion are configured as the same member.
According to this configuration, the enlarged flow path portion and the second throttle portion are the same member. Therefore, it is easy to assemble a path that functions as a muffler.
A compressor according to a fifth aspect of the present invention is the compressor according to any one of the first aspect to the third aspect of the present invention, wherein the first throttle portion, the enlarged flow path portion, and the second throttle portion are configured as separate members.
According to this configuration, the first throttle portion, the enlarged flow path portion, and the second throttle portion are configured as separate members. Therefore, a specification of the path functioning as the muffler can be easily modified by replacing the parts thereof.
A compressor according to a sixth aspect of the present invention is the compressor according to any one of the first aspect to the fifth aspect of the present invention, wherein the enlarged flow path portion is composed of a plurality of members.
According to this configuration, the enlarged flow path portion is composed of a plurality of members. Therefore, it is easy to adjust a length, a flow path cross-sectional area, a radius of curvature, and the like of the enlarged flow path portion by replacing the parts thereof.
A compressor according to a seventh aspect of the present invention is the compressor according to any one of the first aspect to the sixth aspect of the present invention, wherein the flow path cross-sectional area of the enlarged flow path portion is 1.5 times or more, preferably 4.0 times or more, larger than the flow path cross-sectional area of the first throttle portion.
According to this configuration, a ratio of the flow path cross-sectional area of the enlarged flow path portion to the first throttle portion is 1.5 times or more, preferably 4.0 times or more. Therefore, vibrations are effectively reduced.
A compressor according to an eighth aspect of the present invention is the compressor according to any one of the first aspect to the seventh aspect of the present invention, wherein the flow path cross-sectional area of the enlarged flow path portion is 1.5 times or more, preferably 4.0 times or more, larger than the flow path cross-sectional area of the second throttle portion.
According to this configuration, a ratio of the flow path cross-sectional area of the enlarged flow path portion to the second throttle portion is 1.5 times or more, preferably 4.0 times or more. Therefore, vibrations are more effectively reduced.
A compressor according to a ninth aspect of the present invention is the compressor according to any one of the first aspect to the eighth aspect of the present invention, wherein a length of the first throttle portion is not less than 20 mm and not more than 200 mm.
According to this configuration, the first throttle portion ensures a predetermined length. Therefore, vibrations are more effectively reduced.
A compressor according to a tenth aspect of the present invention is the compressor according to any one of the first aspect to the ninth aspect of the present invention, wherein a length of the enlarged flow path portion is not less than 50 mm and not more than 400 mm.
According to this configuration, the enlarged flow path portion ensures a predetermined length. Therefore, vibrations are more effectively reduced.
A compressor according to an eleventh aspect of the present invention is the compressor according to any one of the first aspect to the tenth aspect of the present invention, wherein the compression element includes a fixed scroll and a movable scroll defining the compression chamber. The refrigerant that has exited the second throttle portion enters the compression chamber via the fixed scroll.
According to this configuration, the refrigerant passes through the fixed scroll. Therefore, the refrigerant is stably supplied to the compression chamber defined by the fixed scroll.
A compressor according to a twelfth aspect of the present invention is the compressor according to any one of the first aspect to the tenth aspect, wherein the compression element includes a fixed scroll and a movable scroll that define a compression chamber, and a support member that directly or indirectly supports the fixed scroll. The refrigerant that has exited the second throttle portion enters the compression chamber via the support member.
According to this configuration, the refrigerant passes through the support member.
Therefore, the refrigerant is stably supplied to the compression chamber defined by the fixed scroll via the support member.
A compressor according to a thirteenth aspect of the present invention is the compressor according to any one of the first aspect to the tenth aspect of the present invention, wherein the compression element includes a fixed scroll and a movable scroll defining a compression chamber, and a chamber forming member for defining a chamber together with the fixed scroll.
The chamber functions as a flow path for the high-pressure refrigerant discharged from the compression chamber. The refrigerant that has exited the second throttle portion enters the compression chamber via the chamber forming member.
According to this configuration, the refrigerant passes through the chamber forming member. Therefore, the refrigerant is stably supplied to the compression chamber defined by the fixed scroll via the chamber forming member.
A compressor according to a fourteenth aspect of the present invention is the compressor according to any one of the first aspect to the thirteenth aspect of the present invention further including a third throttle portion that receives the refrigerant from the second throttle portion and guides the refrigerant to the compression chamber. The third throttle portion has a flow path cross-sectional area that is narrower than the flow path cross-sectional area of the second throttle portion.
According to this configuration, the compressor includes a third throttle portion. Therefore, when the refrigerant flows from the second throttle portion to the third throttle portion, the pulsation of the refrigerant can be further reduced.
A compressor according to a fifteenth aspect of the present invention is the compressor according to any one of the first aspect to the fourteenth aspect of the present invention, wherein the first throttle portion includes a valve that is electrically, magnetically, or pneumatically driven.
According to this configuration, the first throttle portion is a valve whose opening/closing and opening degree are controlled. Therefore, the arrangement of the controllable valve enables the first throttle portion to be easily configured.
According to the compressor of the present invention, the vibrations of each part caused by the pressure pulsation of the refrigerant are reduced.
Hereinafter, compressors according to exemplary embodiments of the present invention will be described with reference to the drawings. It should be noted that a specific configuration of a compressor according to the present invention is not limited to the embodiments described hereinafter, can be appropriately changed without departing from the gist of the present invention.
The outdoor unit 60 functions as a heat source. The outdoor unit 60 includes a compressor 10, a four-way switching valve 61, an outdoor heat exchanger 62, an outdoor expansion valve 63, an economizer heat exchanger 64, an injection expansion valve 65, a liquid shutoff valve 67, and a gas shutoff valve 68.
The compressor 10 is a compressor for compressing a refrigerant that is a fluid. The compressor 10 compresses a gaseous low-pressure refrigerant sucked from a suction pipe 21 and discharges a gaseous high-pressure refrigerant from a discharge pipe 22. The four-way switching valve 61 forms a connection indicated by a solid line during a cooling operation and forms a connection indicated by a broken line during a heating operation. The outdoor heat exchanger 62 performs heat exchange between the refrigerant and the air using a fan (not shown), and functions as a condenser during the cooling operation and as an evaporator during the heating operation. The outdoor expansion valve 63 is a valve whose opening degree is adjustable, and functions as a decompressor of the refrigerant. The liquid shutoff valve 67 and the gas shutoff valve 68 are openable and closable valves that are to be closed during maintenance or the like of the air conditioner.
The economizer heat exchanger 64 supercools the liquid refrigerant discharged from the condenser of the refrigerant. The economizer heat exchanger 64 includes a main path 64a and an auxiliary path 64b. The main path 64a is a path through which the liquid refrigerant to be subjected to supercooling passes. The auxiliary path 64b is a path through which a gas refrigerant that acts as a cold heat source necessary for a supercooling operation passes. The gas refrigerant acting as this cold heat source is an intermediate pressure gas refrigerant produced by the injection expansion valve 65 decompressing the liquid refrigerant. The intermediate pressure gas refrigerant leaving the auxiliary path 64b is guided to the compressor 10 by an injection pipe 69.
The indoor unit 80 adjusts the temperature of the air in the room where there is a user present. The indoor unit 80 includes an indoor heat exchanger 81 and an indoor expansion valve 82. The indoor heat exchanger 81 performs heat exchange between the refrigerant and the air using a fan (not shown), and functions as an evaporator during the cooling operation and as a condenser during the heating operation. The indoor expansion valve 82 is a valve whose opening degree is adjustable, and functions as a decompressor of the refrigerant.
The refrigerant piping 70 functions as a path for moving the refrigerant between the outdoor unit 60 and the indoor unit 80. The refrigerant piping 70 includes a liquid refrigerant pipe 71 and a gas refrigerant pipe 72. The liquid refrigerant pipe 71 is a pipe for allowing the liquid shutoff valve 67 and the indoor expansion valve 82 to communicate with each other, and mainly moves the liquid refrigerant or the gas-liquid two-phase refrigerant. The gas refrigerant pipe 72 is a pipe for allowing the gas shutoff valve 68 and the indoor heat exchanger 81 to communicate with each other and mainly moves the gas refrigerant.
Returning to
The compression element 30 is a mechanism for compressing the gas refrigerant. The compression element 30 includes a fixed scroll 31 and a movable scroll 32. The fixed scroll 31 is directly or indirectly fixed to the pressure vessel 20. The movable scroll 32 is revolvable with respect to the fixed scroll. A compression chamber 33 is defined by the fixed scroll 31 and the movable scroll 32. As the movable scroll 32 revolves, the volume of the compression chamber 33 changes to thereby compress the gas refrigerant. The high-pressure gas refrigerant that has undergone the compression process exits the compression element 30 and moves toward a chamber 35 to be described later.
The chamber forming member 34 divides the inner space of the pressure vessel 20 into a chamber 35 and a space 36 outside of the chamber The chamber 35 is filled with the high-pressure gas refrigerant and is a space that functions as a flow path for the high-pressure gas refrigerant. The space outside the chamber is a space filled with the low-pressure gas refrigerant. The motor 40, the crankshaft 43, the first support member 44, and the second support member 45 are attached to the chamber 35.
The motor 40 receives electric power to generate power for the compression element 30. The motor 40 includes a stator 41 and a rotor 42. The stator 41 is directly or indirectly fixed to the pressure vessel 20. The rotor 42 can rotate by performing a magnetic interaction with the stator 41.
The crankshaft 43 transmits the power generated by the motor 40 to the compression element 30. The crankshaft 43 is fixed to the rotor 42 and rotates together with the rotor 42. The crankshaft 43 includes an eccentric portion 43a that is coupled to the movable scroll 32. As the crankshaft 43 rotates, the eccentric portion 43a revolves, thereby causing the movable scroll 32 to revolve.
The first support member 44 directly or indirectly supports the fixed scroll 31. The first support member 44 is directly or indirectly fixed to the pressure vessel 20. The first support member 44 supports a first bearing 44b, and the first bearing 44b pivotally supports the crankshaft 43.
The second support member 45 is directly or indirectly fixed to the pressure vessel 20. The second support member 45 supports a second bearing 45b, and the second bearing 45b pivotally supports the crankshaft 43.
The injection pipe connecting portion 51 is a rigid body, and a first throttle portion S1 having a relatively small flow path cross-sectional area is formed therein. The extension pipe 52 is a metal pipe. The compression element connecting portion 53 is a rigid body, and an enlarged flow path portion E having a relatively large flow path cross-sectional area and a second throttle portion S2 having a relatively small flow path cross-sectional area are formed therein. The compression element connecting portion 53 is fixed to one or both of the pressure vessel 20 and the compression element 30. A distal end of the compression element connecting portion 53 is embedded in the fixed scroll 31. At this distal end, an end portion of the second throttle portion S2 forms an injection spray hole 54. A refrigerant path 31a that allows the second throttle portion and the compression chamber 33 to communicate with each other is formed in the fixed scroll 31. The injection spray hole 54 is connected to this refrigerant path 31a. At least a part of the second throttle portion S2 is provided in the pressure vessel 20.
The flow path cross-sectional area AS1 of the first throttle portion S1 is narrower than both the flow path cross-sectional area A1 of the injection pipe 69 and the flow path cross-sectional area AE of the enlarged flow path portion E. The flow path cross-sectional area AE of the enlarged flow path portion E is larger than both the flow path cross-sectional area AS1 of the first throttle portion S1 and the flow path cross-sectional area AS2 of the second throttle portion S2. The ratio AE/AS1 of the flow path cross-sectional areas AE and AS1 of the enlarged flow path portion E and the first throttle portion S1 is preferably 1.5 or more, and more preferably 4.0 or more. The ratio AE/AS2 of the flow path cross-sectional areas AE and AS2 of the enlarged flow path portion E and the second throttle portion S2 is preferable 1.5 or more, and more preferable 4.0 or more.
The length LS1 of the first throttle portion S1 is not less than 20 mm and not more than 200 mm.
The length LE of the enlarged flow path portion E is not less than 50 mm and not more than 400 mm.
(4-1)
The first throttle portion S1, the enlarged flow path portion E, and the second throttle portion S2 have different flow path cross-sectional areas AS1. AE, and AS2, respectively. Thus, the path composed of the first throttle portion S1, the enlarged flow path portion E, and the second throttle portion S2 functions as a muffler and reduces the vibration of each portion caused by the pressure pulsation of the refrigerant.
(4-2)
At least a part of the second throttle portion S2 is provided in the pressure vessel 20. Therefore, a part of the flow of the pulsating refrigerant passes through the compression vessel whereby the noise outside the pressure vessel is reduced.
(4-3)
A portion of the enlarged flow path portion E and the second throttle portion are the same member. Therefore, it is easy to assemble a path functioning as a muffler.
(4-4)
The ratio AE/AS1 of the flow path cross-sectional areas AE and AS1 of the enlarged flow path portion E and the first throttle portion S1 is 1.5 or more, preferably 4.0 or more. Therefore, vibrations are effectively reduced.
(4-5)
The ratio AE/AS2 of the flow path cross-sectional areas AE and AS2 of the enlarged flow path portion E and the second throttle portion S2 is 1.5 or more, preferably 4.0 or more. Therefore, vibrations are more effectively reduced.
(4-6)
The first throttle portion S1 ensures a predetermined length. Therefore, vibrations are more effectively reduced.
(4-7)
The enlarged flow path portion E ensures the predetermined length LE. Therefore, vibrations are more effectively reduced.
(4-8)
The refrigerant passes through the fixed scroll 31. Therefore, the refrigerant is stably supplied to the compression chamber 33 defined by the fixed scroll 31.
Hereinafter, modification examples of the present exemplary embodiment will be described.
In the above described exemplary embodiment, a portion of the enlarged flow path portion E and the second throttle portion S2 are constituted by the same member, that is, the compression element connecting portion 53. Alternatively, as shown in
According to this configuration, the first throttle portion, the enlarged flow path portion, and the second throttle portion are configured as separate members. Therefore, a specification of the path functioning as the muffler can be easily modified by replacing the parts thereof.
In the above described exemplary embodiment, the enlarged flow path portion E is provided outside the pressure vessel 20. Alternatively, as shown in
According to this configuration, at least a part of the enlarged flow path portion E is provided in the pressure vessel 20. Therefore, a pressure fluctuation of the refrigerant flowing from the enlarged flow path portion E to the second throttle portion S2 occurs in the pressure vessel 20, whereby the noise outside the pressure vessel 20 is reduced.
In the first example modification shown in
According to this configuration, the enlarged flow path portion E is composed of the plurality of members 52a, 52b, and 52c. Therefore, it is easy to adjust a length, a flow path cross-sectional area, a radius of curvature, and the like of the enlarged flow path portion E by replacing the parts thereof.
In the above exemplary embodiment, the first throttle portion S1 is merely composed of a rigid member. As an alternative to this, as shown in
According to this configuration, the first throttle portion S1 is a valve whose opening/closing or opening degree is controlled. Consequently, the arrangement of the controllable valve enables the first throttle portion to be easily configured.
In the above exemplary embodiment, the compressor 10 is a scroll compressor. Alternatively, the compressor 10 may be a rotary compressor or other types of compressor.
In the above exemplary embodiment, the vibration of the injection pipe 69 is reduced by installing the injection pipe connecting portion 51, the extension pipe 52, and the compression element connecting portion 53. As an alternative to this, reducing the vibrations of the suction pipe 21 or the discharge pipe 22 may be realized by providing similar members in the suction pipe 21 or the discharge pipe 22.
A valve structure may be provided in the second throttle portion S2. The valve structure may be a check valve.
The first throttle portion S1, the enlarged flow path portion E. and the second throttle portion S2 are formed of separate members. Furthermore, the enlarged flow path portion E is constituted by a plurality of members 52a and 52b.
(2-1)
With the inclusion of the third throttle portion S3 in the injection path, the pulsation of the refrigerant can be further reduced when the refrigerant flows from the second throttle portion S2 to the third throttle portion S3.
(2-2)
The first throttle portion S1 the enlarged flow path portion E, and the second throttle portion S2 are configured as separate members. Therefore, a specification of the path functioning as the muffler can be easily modified by replacing the parts thereof.
(2-3)
The enlarged flow path portion E is constituted by the plurality of members 52a and 52b. Therefore, a length, a flow path cross-sectional area, a radius of curvature, and the like of the enlarged flow path portion E can be easily adjusted by replacing the parts thereof.
(3-1)
A valve structure may be provided in the second throttle portion S2 or the third throttle portion S3. The valve structure may be a check valve.
(3-2)
The respective example modifications of the first exemplary embodiment may be applied independently or in combination to the present exemplary embodiment.
According to this configuration, the refrigerant passes through the first support member 44. Therefore, the refrigerant is stably supplied to the compression chamber 33 defined by the fixed scroll 31 via the first support member 44.
The various modifications of the above exemplary embodiments may be applied independently or in combination to the present exemplary embodiment.
In the present exemplary embodiment, only the second throttle portion S2 is disposed in the pressure vessel 20.
According to this configuration, the refrigerant passes through the chamber forming member 34. Therefore, the refrigerant is stably supplied to the compression chamber 33 defined by the fixed scroll 31 via the chamber forming member 34.
As shown in
The various modifications of the above exemplary embodiments may be applied independently or in combination to the present exemplary embodiment.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2016-139666 | Jul 2016 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2017/025761 | 7/14/2017 | WO | 00 |
