Patent Application
20250003411
The present disclosure relates to a compressor.
For example, in a scroll compressor that is a kind of a compressor, a compression chamber in which a refrigerant is compressed and a discharge chamber in which the compressed refrigerant is discharged are separated by an end plate, and a discharge port that allows the compression chamber and the discharge chamber to communicate with each other is formed on the end plate. In addition, the end plate is provided with a discharge valve (check valve) that opens and closes a discharge opening and a retainer that regulates an amount of deflection of the discharge valve (for example, refer to PTL 1).
The discharge valve closes the discharge opening in a case where the discharge valve is stopped and opens the discharge opening by bending a tip portion to be warped upward in a case where a pressure in the compression chamber is a predetermined pressure or more. Then, in a case where the pressure in the compression chamber decreases, the discharge valve returns to the discharge valve's original position and closes the discharge opening again. That is, during an operation of the compressor, the tip portion of the discharge valve repeatedly performs reciprocating motion between the end plate and the retainer.
In a case where the pressure in the compression chamber starts to decrease and the discharge valve tends to return to the discharge valve's original position (position at which discharge opening is closed), some of the refrigerant in the discharge chamber may flow back to the compression chamber through the discharge port. In a case where the discharge valve closes the discharge opening in a case where the above-described flowback occurs, the backflowing refrigerant is dammed by the discharge valve, and due to the same principle as that of a so-called water hammer, a pressure of the refrigerant in a space formed between the discharge valve and the retainer may rise sharply, so that a pressure gradient may increase.
The inventors obtained a finding in which the above-described pressure gradient tends to easily propagate in a longitudinal direction (direction from tip toward base end) of the retainer, through analysis and the like. Further, the inventors have found that pressure pulsation occurs in the space formed between the discharge valve and the retainer due to a propagation of the above-described pressure gradient, so that vibration or noise occurs.
The present disclosure has been made in view of the above-described circumstances and an object of the present disclosure is to suppress a rise in the pressure of the refrigerant in the space formed between the discharge valve and the retainer to reduce the vibration and the noise.
In order to solve the above problems, the compressor of the present disclosure adopts the following means.
That is, according to an aspect of the present disclosure, there is provided a compressor including: a partition wall in which a discharge port allowing a compression chamber and a discharge chamber to communicate with each other is formed; a discharge valve that opens and closes a discharge opening on a discharge chamber side of the discharge port, which is located on the discharge chamber side; and a retainer that regulates an amount of deflection of the discharge valve, in which the retainer includes a through-hole that penetrates an upper surface and a lower surface of the retainer, and the through-hole is formed directly above the discharge opening and directly above a portion of the partition wall in which the discharge opening is not formed.
According to the present disclosure, it is possible to suppress the rise in the pressure of the refrigerant in the space formed between the discharge valve and the retainer.
Hereinafter, a compressor according to an embodiment of the present disclosure will be described with reference to the drawings.
A compressor 1 is, for example, a scroll compressor included in an air conditioning device mounted in a vehicle. In the following description, the “compressor 1” will be referred to as a “scroll compressor 1”.
As shown in
The housing 10 includes a motor case 11, an upper case 12, and a lower case 13.
The motor case 11 is a metal tubular member that has opening ends.
The motor case 11 accommodates the compression mechanism 30, the crank shaft 40, and the electric motor 50 inside.
The upper case 12 is a metal member that closes one of the opening ends of the motor case 11.
The upper case 12 is fastened to the motor case 11 and a fixed scroll 31 (described later).
The lower case 13 is a metal member that closes the other end of the opening ends of the motor case 11.
The lower case 13 is fastened to the motor case 11.
An inverter cover 13a is attached to the lower case 13. An inverter (not shown) is accommodated in a space defined by the lower case 13 and the inverter cover 13a.
The compression mechanism 30, the crank shaft 40, the electric motor 50, and various other devices are accommodated in a space defined by the housing 10 (motor case 11, upper case 12, and lower case 13) configured as described above.
The compression mechanism 30 is a mechanism that compresses a low-pressure gas refrigerant taken in from the outside of the housing 10.
The compression mechanism 30 includes the fixed scroll 31 and an orbiting scroll 32.
The fixed scroll 31 is a member that includes a fixed end plate (partition wall) 31a and a scroll-shaped fixed wall 31b erected from the fixed end plate 31a.
The fixed scroll 31 is fastened to the upper case 12 and defines a discharge chamber 35 between the fixed scroll 31 and the upper case 12. A discharge pipe (not shown) is connected to the discharge chamber 35, and is configured to be able to supply the compressed gas refrigerant to the outside of the scroll compressor 1.
A discharge port 37 is formed in the fixed end plate 31a, and allows the discharge chamber 35 and a compression chamber 36 (described later) that are separated by the fixed end plate 31a to communicate with each other.
The discharge port 37 is a circular hole that penetrates in a thickness direction of the fixed end plate 31a at an approximately center portion (position corresponding to space in which pressure of refrigerant is highest in compression chamber 36) of the fixed end plate 31a.
In the discharge chamber 35, a discharge valve 70 and a retainer 80 that regulates an amount of deflection of the discharge valve 70 are provided at an outlet (discharge opening 37a) of the discharge port 37. The discharge valve 70 and the retainer 80 will be described later in detail.
The orbiting scroll 32 is a member that includes an orbiting end plate 32a and a scroll-shaped orbiting wall 32b erected from the orbiting end plate 32a.
The orbiting scroll 32 is configured to perform revolving and orbiting motion with respect to the fixed scroll 31 by means of the crank shaft 40 rotating around an axis X1 and a known rotation prevention mechanism.
Each of walls of the fixed scroll 31 and the orbiting scroll 32 are meshed with each other, so that the compression chamber 36 is formed.
The gas refrigerant taken in from the outside of the housing 10 by a suction pipe (not shown) is introduced into the compression chamber 36. The compression chamber 36 is configured such that a volume is gradually reduced by the revolving and orbiting motion of the orbiting scroll 32, and is configured such that the gas refrigerant is compressed accordingly.
The crank shaft 40 is a member for transmitting driving force from the electric motor 50 to the orbiting scroll 32.
The crank shaft 40 includes a shaft body 40a and a crank pin 40b. The shaft body 40a and the crank pin 40b are integrally formed as the crank shaft 40.
The shaft body 40a is a shaft-shaped member that extends along the axis X1. The shaft body 40a is rotationally driven around the axis X1 by the electric motor 50.
The shaft body 40a is rotatably supported around the axis X1 by a main bearing 61 disposed on an upper case 12 side and by a sub bearing 62 disposed on a lower case 13 side.
The crank pin 40b is a shaft-shaped member that is provided at an end portion of the shaft body 40a.
The crank pin 40b extends along an axis X2 that is eccentric with respect to the axis X1.
In the crank shaft 40 configured as described above, the orbiting scroll 32 is driven by connecting the crank pin 40b to the orbiting scroll 32 and by rotationally driving the shaft body 40a around the axis X1 by means of the electric motor 50, so that the gas refrigerant is compressed by the compression mechanism 30.
As shown in
As shown in
An outer shape of the discharge valve 70 approximately coincides with an outer shape of the retainer 80 in a case where the outer shape of the discharge valve 70 is viewed in a plan view.
The retainer 80 is a plate-shaped member that is provided to overlap with the discharge valve 70.
As shown in
In
As shown in
The tip 80a of the retainer 80 is positioned above the base end 80b, and the outer shape of the retainer 80 has a form of gradually warping from the base end 80b toward the tip 80a in a case where the outer shape of the retainer 80 is viewed from a side surface.
The discharge valve 70 closes the discharge opening 37a of the discharge port 37 in a case where the scroll compressor 1 is stopped, and opens the discharge opening 37a by bending the tip 70a to be warped upward in a case where an operation of the scroll compressor 1 is started, so that a pressure in the compression chamber 36 is a predetermined pressure or more (discharge valve 70 shown by broken line in
In addition, in a case where the pressure in the compression chamber 36 decreases, the discharge valve 70 returns to the discharge valve 70's original position and closes the discharge opening 37a again.
That is, during the operation of the scroll compressor 1, the tip 70a of the discharge valve 70 repeatedly performs reciprocating motion between the fixed end plate 31a and the retainer 80.
In the discharge valve 70 and the retainer 80 that are configured in the above-described manner, in a case where the pressure in the compression chamber 36 starts to decrease and the discharge valve 70 tends to return to the discharge valve 70's original position (position at which discharge opening 37a is closed), some of the refrigerant in the discharge chamber 35 may flow back to the compression chamber 36 through the discharge port 37. In a case where the discharge valve 70 closes the discharge opening 37a in a case where the above-described flowback occurs, the backflowing refrigerant is dammed by the discharge valve 70, and a pressure of a refrigerant in a space formed between the discharge valve 70 and the retainer 80 may rise sharply, so that a pressure gradient may increase.
The inventors obtained a finding in which the above-described pressure gradient tends to easily propagate in a longitudinal direction (direction from tip 80a toward base end 80b) of the retainer 80, through analysis and the like.
Therefore, in the present embodiment, in order to suppress a pressure rise or a pressure gradient propagation of the refrigerant in the space formed between the discharge valve 70 and the retainer 80, a through-hole 81 is formed in the retainer 80.
Hereinafter, a configuration of the through-hole 81 will be described with reference to a plurality of examples.
As shown in
As shown in
It is preferable that a base end 81b of the through-hole 81 reaches an intermediate position between the tip 80a and the base end 80b of the retainer 80 or a position closer to the base end 80b with respect to the intermediate position.
The through-hole 81 configured as described above has a longitudinal dimension (dimension from tip 81a to base end 81b) that is equal to or larger than a diameter of the discharge opening 37a, that is preferably 1.5 times or more the diameter of the discharge opening 37a, and that is more preferably 2 times or more the diameter of the discharge opening 37a.
However, in a case where the base end 81b of the through-hole 81 is too close to the base end 80b of the retainer 80, there is a possibility that strength of the retainer 80 is insufficient. Therefore, it is necessary to appropriately design the retainer 80 in consideration of a dimension or a shape of the retainer 80.
As shown in
The tip 81a of the through-hole 81 may reach an edge of the tip 80a of the retainer 80. That is, the through-hole 81 may be a notch that is formed in a U shape from the tip 80a of the retainer 80.
Even in the above-described case, it is preferable that the base end 81b of the through-hole 81 reaches the intermediate position between the tip 80a and the base end 80b of the retainer 80 or the position closer to the base end 80b with respect to the intermediate position.
As shown in
However, unlike in Example 1 and Example 2, the through-hole 81 of the present example is not configured by one hole that is integrally formed from the tip 80a toward the base end 80b of the retainer 80, but is configured by a plurality of circular holes that are provided in the longitudinal direction of the retainer 80.
According to the present embodiment, the following effects are achieved.
Since the retainer 80 includes the through-hole 81 that penetrates the upper surface and the lower surface of the retainer 80, it is possible to release the refrigerant in the space formed between the discharge valve 70 and the retainer 80 to an upper surface side of the retainer 80 via the through-hole 81. As a result, it is possible to suppress the rise in the pressure of the refrigerant in the space and a pressure pulsation caused by the rise in the pressure.
Further, since the through-hole 81 is formed directly above the discharge opening 37a and directly above the portion of the fixed end plate 31a in which the discharge opening 37a is not formed, it is possible to release the refrigerant to the upper surface side of the retainer 80 in a range along a direction in which the pressure gradient is easily propagated, including directly above the discharge opening 37a where the pressure easily rises.
Further, as in Example 1 and Example 2, in a case where the through-hole 81 is integrally formed along the longitudinal direction of the retainer 80 and where the base end 81b of the through-hole 81 reaches the intermediate position between the tip 80a and base end 80b of the retainer 80 or the position closer to the base end 80b with respect to the intermediate position, it is possible to more efficiently release the refrigerant to the upper surface side of the retainer 80.
As shown in
In this case, it is possible to secure a large area (opening area) of a portion that functions as the through-hole 81 without placing the through-hole 81 close to the base end 80b of the retainer 80. Therefore, it is possible to further suppress the pressure rise and the pressure pulsation caused by the pressure rise.
Further, as shown in
In this case, it is possible to secure the area (opening area) of the portion that functions as the through-hole 81 without placing the through-hole 81 close to the base end 80b of the retainer 80.
The embodiments described above are understood as follows, for example.
That is, according to an aspect of the present disclosure, there is provided a compressor (1) including: a partition wall (31a) in which a discharge port (37) allowing a compression chamber (36) and a discharge chamber (35) to communicate with each other is formed; a discharge valve (70) that opens and closes a discharge opening (37a) on a discharge chamber side of the discharge port, which is located on the discharge chamber side; and a retainer (80) that regulates an amount of deflection of the discharge valve, in which the retainer includes a through-hole (81) penetrating an upper surface and a lower surface of the retainer, and the through-hole is formed directly above the discharge opening and directly above a portion of the partition wall in which the discharge opening is not formed.
According to the present aspect, there is provided a compressor including: a partition wall in which a discharge port allowing a compression chamber and a discharge chamber to communicate with each other is formed; a discharge valve that opens and closes a discharge opening on a discharge chamber side of the discharge port, which is located on the discharge chamber side; and a retainer that regulates an amount of deflection of the discharge valve, in which the retainer includes a through-hole that penetrates an upper surface and a lower surface of the retainer; therefore it is possible to release a refrigerant in a space formed between the discharge valve and the retainer to an upper surface side of the retainer via the through-hole. As a result, it is possible to suppress the rise in the pressure of the refrigerant in the space and a pressure pulsation caused by the rise in the pressure.
Further, since the through-hole is formed directly above the discharge opening and directly above the portion of the partition wall in which the discharge opening is not formed, it is possible to release the refrigerant to the upper surface side of the retainer in a range along a direction in which the pressure gradient is easily propagated, including directly above the discharge opening where the pressure easily rises.
In addition, according to an embodiment of the present disclosure, there is provided the compressor, in which the retainer has a tongue-like shape that extends from a base end (80b) fixed to the partition wall toward a tip (80a), and the through-hole is integrally formed from a position directly above the discharge opening toward the base end along an extending direction of the retainer.
According to the present aspect, there is provided the compressor, in which the retainer has a tongue-like shape that extends from a base end fixed to the partition wall toward a tip, and the through-hole is integrally formed from a position directly above the discharge opening toward the base end along an extending direction of the retainer; therefore it is possible to provide a through-hole extending along a direction in which a pressure gradient is easily propagated. As a result, it is possible to efficiently release the refrigerant to the upper surface side of the retainer.
In addition, according to an embodiment of the present disclosure, there is provided the compressor, in which the through-hole is integrally formed at least from the position directly above the discharge opening to an intermediate position between the tip and the base end.
According to the present aspect, there is provided the compressor, in which the through-hole is integrally formed at least from the position directly above the discharge opening to an intermediate position between the tip and the base end; therefore it is possible to provide a through-hole having sufficient dimensions along a direction in which a pressure gradient is easily propagated. As a result, it is possible to efficiently release the refrigerant to the upper surface side of the retainer.
Further, according to an embodiment of the present disclosure, there is provided the compressor, in which the through-hole has a notch shape that extends from an edge of the tip of the retainer toward a base end side of the retainer.
According to the present aspect, there is provided the compressor, in which the through-hole has a notch shape that extends from an edge of the tip of the retainer toward a base end side of the retainer; therefore it is possible to provide a through-hole having sufficient dimensions further along a direction in which a pressure gradient is easily propagated. As a result, it is possible to efficiently release the refrigerant to the upper surface side of the retainer.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2021-170776 | Oct 2021 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2022/038620 | 10/17/2022 | WO |
