Patent Application
20170097002
The present invention relates to a fluid compressor.
A scroll compressor is known in which a discharge valve for a high-pressure space of a chamber is provided in a closed container (see Patent Literature 1, for example).
Patent Literature 1: Japanese Patent No. 4189751 (pages 3 and 4, FIG. 1)
A discharge valve prevents gas discharged from a helix from flowing back into the helix. Such discharge valves are roughly categorized into two types. One of the two types of discharge valves is a float-type valve (a float valve) that is freely movable in a space and is not fixed. The other of the two types of discharge valves is a cantilever-type valve (a reed valve) with one end fixed. The two types of discharge valves are different in the direction of discharge, in the discharging area, and in the valve-closing speed. Consequently, an appropriate discharge valve is employed depending on the flow rate of discharge of refrigerant and pressure conditions.
However, the behavior of the float valve is unstable, thus the float valve is rarely employed. On the other hand, the reed valve has at least one of two ends fixed to a closed container. Hence, the behavior of the reed valve is more stable than the behavior of the float valve. Furthermore, the reed valve rarely causes a delay in the closing action and can prevent the backflow. In a case where the reed valve is provided in a fluid compressor, however, when the cross-sectional area of a passage at a discharge port that allows refrigerant compressed in a compression chamber to flow through the discharge port is increased, the length of the reed valve needs to be increased. Consequently, in a compressor including a small closed container, providing a reed valve in the closed container is difficult.
A fluid compressor including a reed valve is provided with a valve retainer. The valve retainer limits the amount of lift of the reed valve and the curvature of the reed valve, thereby reducing the stress occurring in the reed valve. Hence, providing a valve retainer prevents the excessive lifting of the reed valve that may break the reed valve from the base. The shape of the valve retainer is determined so that the bending stress occurring in the reed valve when the reed valve is lifted along the curve of the valve retainer is smaller than or equal to an allowable stress. The amount of lift of the reed valve is defined by the length of the reed valve from the fixed part to the tip to be lifted and the allowable curvature of the reed valve.
When a reed valve and a valve retainer are provided in a limited space in a closed container included in a fluid compressor, the reed valve cannot have a satisfactory length. Thus, the amount of lift of the reed valve is naturally small. Consequently, the fluid compressed in a compression chamber is discharged from a narrow discharge passage. That is, the refrigerant compressed in the compression chamber and discharged from the compression chamber flows through the narrow discharge passage, thus the pressure loss increases. Consequently, the pressure increases extraordinarily on the upstream side of the discharge valve. When the refrigerant is compressed with the extraordinarily high pressure on the upstream side of the discharge valve, the temperature of the refrigerant tends to rise. Consequently, the reliability of the compressor may be lowered.
When R32 refrigerant or a refrigerant mixture containing R32 refrigerant by 51% or higher is used, the pressure of the refrigerant tends to become higher, because of its characteristics, even within a range of normal use, than in a case where R410A refrigerant containing R32 refrigerant by 50% is used. Consequently, in a fluid compressor configured as described above, the pressure of the refrigerant is more likely to increase. Furthermore, in the case where R32 refrigerant or a refrigerant mixture containing R32 refrigerant by 51% or higher is used, the temperature of the refrigerant is generally higher by 10 to 30 degrees C. than the discharge temperature of the R410A refrigerant containing R32 refrigerant by 50%
Hence, when the discharge pressure or the discharge temperature tends to become high in the case where R32 refrigerant or a refrigerant mixture containing R32 refrigerant by 51% or higher is used, the discharge pressure or the discharge temperature may be detected, and, on the basis of the result of such detection, the compressor may be controlled to be operated so that the discharge pressure or the discharge temperature does not exceed a predetermined level, thus the reliability of the compressor may be maintained. However, when the operation of the compressor is restricted on the basis of the detected discharge pressure or discharge temperature in the case where R32 refrigerant or a refrigerant mixture containing R32 refrigerant by 51% or higher is used, the compressor cannot operate as satisfactorily as in the case where R410A refrigerant is used. Such a problem occurs because as the percentage of R32 refrigerant becomes higher, the pressure of the compressed refrigerant tends to become higher, and the temperature of the refrigerant tends to increase.
When a refrigerant containing carbon double bonds, such as HFO-1234yf refrigerant and HFO-1234ze refrigerant, or a refrigerant mixture containing such a refrigerant by 30% or higher is used, the amount of refrigerant to be circulated needs to be increased to 2- to 2.5-fold to obtain substantially the same level of cooling effect as that obtained by R410A refrigerant. However, when the amount of refrigerant to be circulated is increased, the speed of the refrigerant flowing through the discharge valve is increased, thus increasing the pressure loss. When the pressure loss increases, the pressure extraordinarily increases on the upstream side of the discharge valve, thus extraordinarily raises the discharge temperature. Alternatively, HFO-1123 refrigerant, which is a refrigerant containing carbon double bonds, is highly flammable and is thus used by being mixed with a less flammable refrigerant. When HFO-1123 refrigerant is to be mixed with another refrigerant containing carbon double bonds, such as HFO-1234yf refrigerant and HFO-1234ze refrigerant, or with R32 refrigerant, the mixture containing HFO-1123 by 70% or lower can be safely used. However, when the discharge temperature of such a refrigerant mixture rises, the stability of the refrigerant tends to be reduced.
Hence, when the discharge pressure or the discharge temperature of the refrigerant tends to become high in the case where a refrigerant containing carbon double bonds, such as HFO-1234yf refrigerant and HFO-1234ze refrigerant, is used, the discharge pressure or the discharge temperature may be detected, and, on the basis of the result of such detection, the compressor may be controlled to be operated so that the discharge pressure or the discharge temperature does not exceed a predetermined level, thus the reliability of the compressor may be maintained. However, when the operation of the compressor is restricted on the basis of the result of detected discharge pressure or discharge temperature in the case where a refrigerant containing carbon double bonds, such as HFO-1234yf refrigerant and HFO-1234ze refrigerant, is used, the compressor cannot operate as satisfactorily as in the case where R410A refrigerant is used,
In view of the above, an object of the present invention is to provide a compact fluid compressor in which the pressure loss at the discharge valve is reduced.
A fluid compressor according to an embodiment of the present invention includes a closed container having an inlet, a compression mechanism including a compression chamber in which fluid flowing into the closed container through the inlet is compressed, a discharge port through which the fluid compressed in the compression chamber is allowed to flow, a discharge valve opening and closing the discharge port, and a valve retainer limiting an amount of lift of the discharge valve. The discharge valve includes a curved portion whose shape is defined by one or more curvatures. When the discharge port is closed by the discharge valve, the valve retainer and the discharge valve are spaced apart from each other.
In the fluid compressor according to the embodiment of the present invention, the discharge valve includes the curved portion whose shape is defined by one or more curvatures. Consequently, the discharge valve can be made shorter than in a case of a discharge valve having a straight line shape. Hence, a greater amount of lift can be provided than in the case of the discharge valve having the straight line shape. Thus, the pressure loss can be reduced. In addition, the size can be more reduced than in the case of the discharge valve having the straight line shape.
Scroll compressors as exemplary fluid compressors 100 according to the present invention will be described below. The following configurations, operations, and other associated matter are only exemplary, and the configurations, operations, and other associated matter of the fluid compressors 100 according to the present invention are not limited to the examples. In each of the drawings, the same or similar members or portions are denoted by common reference signs, and details are simplified or omitted appropriately. Redundant or similar description is also simplified or omitted appropriately.
The fixed scroll 1 includes an end plate 1a, and a first helical portion 1b extending from the end plate 1a. The fixed scroll 1 has a discharge port 1f. The discharge port 1f is provided at substantially the center of a surface (the upper surface of the fixed scroll 1) that does not form the helix of the fixed scroll 1. The seal 24 is provided at an end surface of the first helical portion 1b of the fixed scroll 1.
The orbiting scroll 2 includes an end plate 2a, and a second helical portion 2b extending from the end plate 2a. The orbiting scroll 2 houses a key portion (not illustrated) of the Oldham ring 7. The seal 25 is provided at an end surface of the second helical portion 2b of the orbiting scroll 2. The whirling direction of the second helical portion 2b is opposite to the whirling direction of the first helical portion 1b.
The fixed scroll 1 and the orbiting scroll 2 form a compression mechanism of the fluid compressor 100. When the orbiting scroll 2 moves orbitally, a centrifugal force acts on the orbiting scroll 2. Thus, the orbiting scroll 2 slides in a slidable area defined between the eccentric shaft portion 10a of the main shaft 10 and a sliding surface 11a on the inner side of the slider 11. Then, the second helical portion 2b of the orbiting scroll 2 and the first helical portion 1b of the fixed scroll 1 come into contact with and mesh with each other, thus forming a compression chamber 23.
The frame 3 is provided for fixing the fixed scroll 1 and is fixed to a closed container 20. The frame 3 includes the main bearing 4 that bears the rotation of the main shaft 10. The main bearing 4 is provided at, for example, the center of the frame 3. The orbiting bearing 5 is provided at, for example, the rear center of the end plate 2a of the orbiting scroll 2. The thrust plate 6 serves as a thrust bearing that bears the orbiting scroll 2 in the axial direction. The thrust plate 6 is provided on a thrust bearing portion of the frame 3. The Oldham ring 7 prevents the orbiting scroll 2 from rotating on its own axis and allows the orbiting scroll 2 to move orbitally. The electric-motor rotor 8 and the electric-motor stator 9 form an electric motor.
The main shaft 10 is a shaft that is rotated by the electric motor and is provided at, for example, the center of the frame 3. The eccentric shaft portion 10a is a slider-attaching shaft provided at the top of the main shaft 10 so that the slider 11 is eccentric to the main shaft 10. The eccentric shaft portion 10a is provided with the pivot portion 10d. The pump shaft 10b transmits a rotational force to the oil pump 18 and is integrated with the main shaft 10. The main shaft 10 also has the oil hole 10c extending through the center of the main shaft 10 from the lower end of the pump shaft 10b to the upper end of the main shaft 10.
The slider 11 bears the orbiting scroll 2 to allow the orbiting scroll 2 to move orbitally. The sleeve 12 is provided in the vicinity of the eccentric shaft portion 10a and allows the main bearing 4 and the main shaft 10 to rotationally move smoothly. The upper balance-weight portion 13 and the lower balance-weight portion 14 offset the unbalance between the orbiting scroll 2 moved orbitally by the eccentric shaft portion 10a of the main shaft 10 and the center of rotation of the main shaft 10.
The sub-frame 15 is fixed in the closed container 20 and is provided at the bottom of the eccentric shaft portion 10a. A bearing-receiving portion 15a is provided at the center of the sub-frame 15. The sub-frame 15 is provided with the oil pump 18 that is of a displacement type. The outer ring of the sub-bearing 16 is press-fitted in and is secured in the bearing-receiving portion 15a. The oil pump 18 communicates with the oil hole 10c at the lower end of the main shaft 10.
The closed-container middle 20a, the closed-container bottom 20b, and the closed-container top 20c form a container that houses various members of the fluid compressor 100. The closed-container middle 20a secures the frame 3 at the top end and supports the electric-motor stator 9 in a middle part. The closed-container middle 20a has an inlet 21. The closed-container bottom 20b has the oil sump 19 at the bottom. The oil sump 19 is positioned in a space into which refrigerant having a relatively low temperature sucked into the closed-container middle 20a, the closed-container bottom 20b, and the closed-container top 20c flows. The oil sump 19 is filled with lubricating oil that lubricates the bearings. The closed-container top 20c has an outlet 22. The combination of the closed-container middle 20a, the closed-container bottom 20b, and the closed-container top 20c as a whole has, for example, a cylindrical shape.
Hereinafter, the closed-container middle 20a, the closed-container bottom 20b, and the closed-container top 20c are also collectively referred to as the closed container 20. The closed container 20 may alternatively be divided into smaller members or a more number of members, instead of being divided into three members, or may be provided as one integral body.
The inlet 21 is an opening for sucking the refrigerant flowing into a refrigerant pipe on a suction side of the fluid compressor 100 into the closed container 20. The inlet 21 is provided in the vicinity of a suction port of the frame 3, the electric-motor rotor 8, and the electric-motor stator 9. The outlet 22 is an opening for discharging the refrigerant compressed in the closed container 20 to the outside of the closed container 20.
Hereinafter, the end of the discharge valve 26 that closes the discharge port 1f is also referred to as the free end of the discharge valve 26. Hereinafter, the other end of the discharge valve 26 that is fixed to the fixed scroll 1 with the bolt 28 is also referred to as the fixed end of the discharge valve 26.
As illustrated in
The valve retainer 27 is made of, for example, a material that is highly strong and highly tough. Hence, when the discharge valve 26 opens the discharge port 1f and warps upward to collide with the valve retainer 27 or when the valve retainer 27 receives a load caused by the jetted refrigerant gas, the probability that the valve retainer 27 is damaged can be reduced, Herein, the “material that is highly strong and highly tough” is, for example, stainless steel.
In a state where the discharge valve 26 closes the discharge port 1f, the discharge valve 26 and the valve retainer 27 are spaced apart from each other. In a state where the discharge valve 26 opens the discharge port 1f, the discharge valve 26 and the valve retainer 27 are spaced apart from or in contact with each other. When the discharge valve 26 and the valve retainer 27 come into contact with each other, the amount of lift of the discharge valve 26 is limited.
Hereinafter, one end of the valve retainer 27 that is positioned above the free end of the discharge valve 26 is also referred to as the free end of the valve retainer 27. Hereinafter, the other end of the valve retainer 27 that is positioned above the fixed end of the discharge valve 26 is also referred to as the fixed end of the valve retainer 27.
The valve retainer 27 may be formed to curve gently from the fixed end to the free end of the valve retainer 27. Thus, in the state where the discharge valve 26 opens the discharge port 1f, the discharge valve 26 is easily in close contact with the valve retainer 27.
The discharge valve 26 may be coated or nitrided. Thus, even when the discharge valve 26 collides with the fixed scroll 1 or the valve retainer 27, the discharge valve 26 is less likely to wear.
Before the fluid flowing in the closed container 20 is compressed in the compression chamber 23, the discharge port 1f is closed by the discharge valve 26 as illustrated in
The curvature of the valve retainer 27 is determined so that the stress to be applied to the discharge valve 26 is equal to or lower than the allowable stress of the material forming the discharge valve 26. The amount of lift defined by the shape of the valve retainer 27 is set to be as large as possible within a range corresponding to the above curvature so that the resistance of the compressed gas flowing out of the discharge port 1f can be made as small as possible.
The operation of the fluid compressor 100 according to Embodiment 1 will be described below.
When power is supplied to the electric-motor stator 9, the main shaft 10 is rotated by the electric-motor rotor 8. The rotational power is transmitted through the slider 11 housing the eccentric shaft portion 10a to the inside of the orbiting bearing 5 and then to the orbiting scroll 2. Then, the Oldham ring 7 reciprocatingly moves between an Oldham groove (not illustrated) of the orbiting scroll 2 and an Oldham groove (not illustrated) of the frame 3. Hence, the rotation of the orbiting scroll 2 is prevented, and the orbiting scroll 2 moves orbitally.
Variations in the accuracy that may occur when the frame 3 and the sub-frame 15 are fixed to the closed container 20 and variations in the accuracy of each of associated components cause the misalignment between the main bearing 4 and the sub-bearing 16. Furthermore, the main shaft 10 may bend, thus the main bearing 4 and the sub-bearing 16 do not necessarily become parallel to the main shaft 10. Consequently, the sleeve 12 is provided between the main shaft 10 and the main bearing 4 so that the sliding surface on the inner side of the main bearing 4 extends parallel to the main shaft 10 and the sub-bearing 16. Hence, for example, when the misalignment occurs between the main bearing 4 and the sub-bearing 16 and the main shaft 10 is tilted to the main bearing 4, the pivot portion 10e of the main shaft 10 comes into contact with the inner peripheral surface of the sleeve 12 and absorbs the tilt of the main shaft 10. Thus, the outer periphery of the sleeve 12 slides along the main bearing 4 always parallelly.
Furthermore, the load generated by the centrifugal force of the orbiting scroll 2 and the load generated when the refrigerant is compressed and acting in the radial direction are applied to the eccentric shaft portion 10a of the main shaft 10, thus the eccentric shaft portion 10a bends. Consequently, the eccentric shaft portion 10a does not necessarily extend parallel to the inner surface of the orbiting bearing 5. To make the sliding surface of the orbiting bearing 5 to extend parallel to the eccentric shaft portion 10a of the main shaft 10, the slider 11 is provided between the eccentric shaft portion 10a of the main shaft 10 and the orbiting bearing 5. Consequently, for example, when the eccentric shaft portion 10a bends and is tilted to the orbiting bearing 5, the pivot portion 10d comes into contact with the slider surface (not illustrated) of the slider 11 and absorbs the tilt of the eccentric shaft portion 10a. Thus, the outer periphery of the slider 11 slides along the orbiting bearing 5 always parallelly.
The flow of refrigerant and the flow of refrigerating machine oil will be described below.
The refrigerant in a refrigerant circuit is introduced into the closed container 20 through the inlet 21 and flows into the compression chamber 23 through the suction port (not illustrated) of the frame 3. Furthermore, the lubricating oil pumped up by the oil pump 18 is supplied to associated sliding points through the oil hole 10c of the main shaft 10 and flows into the compression chamber 23. Exemplary sliding points are listed below from (1) to (7).
(1) The point between the end plate 2a of the orbiting scroll 2 and the thrust plate 6
(2) The point between the side surface of the first helical portion 1b of the fixed scroll 1 and the side surface of the second helical portion 2b of the orbiting scroll 2
(3) The points between the seal 24 of the fixed scroll 1 and bottom lands of the end plate 2a of the orbiting scroll 2, the bottom lands each provided between adjacent teeth of the second helical portion 2b
(4) The points between the seal 25 of the orbiting scroll 2 and bottom lands of the end plate 1a of the fixed scroll 1, the bottom lands each provided between adjacent teeth of the first helical portion 1b
(5) The point between a projection of the Oldham ring 7 and a groove provided in the frame 3
(6) The point between the projection of the Oldham ring 7 and a groove provided in the end plate 2a of the orbiting scroll 2
(7) The point between the orbiting bearing 5 and the outer peripheral surface of the slider 11, and the point between the main bearing 4 and the outer peripheral surface of the sleeve 12
The lubricating oil lubricates the point between the end plate 2a of the orbiting scroll 2 and the thrust plate 6 and overflows to a side of the end plate 2a of the orbiting scroll 2 on which the second helical portion 2b is provided. The lubricating oil overflowed to the surface of the end plate 2a of the orbiting scroll 2 on which the second helical portion 2b is provided flows into the compression chamber 23 together with the refrigerant flowing from the suction port of the frame 3. The lubricating oil flowed into the compression chamber 23 is used at, for example, the following sliding points (a) to (c).
(a) The point between the side surface of the first helical portion 1b of the fixed scroll 1 and the side surface of the second helical portion 2b of the orbiting scroll 2
(b) The points between the seal 24 of the fixed scroll 1 and bottom lands of the end plate 2a of the orbiting scroll 2, the bottom lands each provided between adjacent teeth of the second helical portion 2b
(c) The points between the seal 25 of the orbiting scroll 2 and bottom lands of the end plate 1a of the fixed scroll 1, the bottom lands each provided between adjacent teeth of the first helical portion 1b
At the above sliding points (a) to (c), the temperature rises with the sliding motion. The sliding points where the temperature rises with the sliding motion are positioned in a space into which refrigerant having a relatively low temperature sucked into the closed container 20 flows. Consequently, the sliding points where the temperature has risen with the sliding motion is cooled by the refrigerant sucked into the closed container 20. The electric-motor rotor 8, the electric-motor stator 9, and other associated components are also cooled by the relatively low-temperature refrigerant sucked into the closed container 20. The refrigerating machine oil that has lubricated the sliding points is also cooled by the relatively low-temperature refrigerant sucked into the closed container 20 in the oil sump 19.
Meanwhile, when the power is supplied to the electric-motor stator 9, the main shaft 10 and the electric-motor rotor 8 are rotated. The power is supplied from, for example, a commercial power supply at 50 Hz or 60 Hz. To make the amount of refrigerant to be circulated variable, an inverter power supply capable of operating at a rotation speed of driving that is variable within the range of 600 rpm to 15000 rpm may be used.
When the main shaft 10 is driven and rotated, the main shaft 10 rotates together. The eccentric shaft portion 10a rotates in the orbiting bearing 5. Furthermore, the orbiting scroll 2 is prevented from rotating on its own axis by the Oldham ring 7. Consequently, only the rotational motion of the eccentric shaft portion 10a is transmitted to the orbiting scroll 2. When the orbiting scroll 2 rotationally moves, the refrigerant and the lubricating oil flowed into the compression chamber 23 move toward the centers of the fixed scroll 1 and the orbiting scroll 2. The refrigerant and the lubricating oil flowed into the compression chamber 23 are compressed because the compression chamber 23 changes its shape and comes to have a reduced volume. In this step, the compressed refrigerant generates a load that moves the fixed scroll 1 and the orbiting scroll 2 away from each other in the axial direction. The load is borne by a bearing formed by the thrust plate 6 from a surface of the end plate 2a of the orbiting scroll 2 that is opposite to the surface on which the second helical portion 2b is provided.
The refrigerant and the lubricating oil compressed in the compression chamber 23 flow through the discharge port 1f and thus push up the discharge valve 26. Thus, the discharge valve 26 opens the discharge port 1f. In this state, the discharge valve 26 is elastically deformed by the jet stream of the refrigerant to extend along the valve retainer 27. The refrigerant and the lubricating oil passing through the discharge port 1f flow through the high-pressure part of the closed container 20 and the outlet 22 in this order and are discharged to the outside of the closed container 20. The refrigerant and the lubricating oil discharged from the outlet 22 to the outside of the closed container 20 flow through the refrigerant circuit (not illustrated) and flow into the closed container 20 again through the inlet 21.
When the fluid compressor 100 is not in operation, the discharge port 1f is closed by the discharge valve 26 with the elastic force of the discharge valve 26. When a pressure difference lies between the upstream side and the downstream side of the discharge port 1f, the pressure difference is added to the force of pressing the discharge valve 26 against the closing portion 26a1, thus the discharge port 1f is closed. When the fluid compressor 100 is in operation, the discharge valve 26 may repeatedly close and open the discharge port 1f, depending on the pressure difference between the upstream side and the downstream side of the discharge valve 26.
As described above, the fluid compressor 100 according to Embodiment 1 includes the discharge valve 26 having a U shape or a substantially U shape. Consequently, the length of the valve retainer 27 from the fixed end to the free end can be made long. Hence, the curvature of the discharge valve 26 can be made large, and the amount of lift of the discharge valve 26 can also be made large. In particular, when the discharge valve 26 is shaped as illustrated in
In Embodiment 1, the diameter of the cylindrical closed container 20 is determined by the size of the motor and the strength against the pressure. Hence, the designed amount of lift of the discharge valve 26 can be optimized in consideration that the discharge valve 26 is housed in the closed container 20. Consequently, the pressure loss in the vicinity of the discharge valve 26 can be reduced.
The pressure loss can be reduced as described above, thus costs do not significantly increase even when any of the following refrigerants is used: refrigerant containing carbon double bonds and tending to flow at a high speed and to cause a large pressure loss, such as HFO-1234yf refrigerant and HFO-1234ze refrigerant; a refrigerant mixture containing refrigerant containing carbon double bonds, such as HFO-1234yf refrigerant, by 30% or higher, and tending to flow at a high speed and to cause a large pressure loss; a refrigerant mixture containing HFO-1123 refrigerant required to be controlled under operational restrictions because the discharge temperature tends to be high by 70% or lower; a refrigerant mixture containing R32 refrigerant; and a refrigerant mixture containing R32 refrigerant by 51% or higher.
The fluid used in the fluid compressor 100 is not limited to a specific fluid. When a refrigerant is used as the fluid, a greater effect of the fluid can be obtained by a refrigerant mixture containing HFC-based R32 refrigerant whose ozone depletion potential is zero, or a refrigerant mixture containing R32 refrigerant by 51% or higher. This is because the pressure of HFC-based R32 refrigerant whose ozone depletion potential is zero or a refrigerant mixture containing R32 refrigerant by 51% or higher easily increases, thus the temperature of such a refrigerant easily rises.
“A refrigerant mixture containing R32 refrigerant by 51% or higher” refers to, for example, a refrigerant mixture obtained by mixing R32 with any of the following: HFC refrigerant whose ozone depletion potential is zero, halogenated hydrocarbon containing carbon double bonds in its refrigerant composition, and hydrocarbon. “HFC refrigerant whose ozone depletion potential is zero” refers to, for example, R125 or R161. “Halogenated hydrocarbon containing carbon double bonds” refers to, for example, fluorocarbon-based low-GWP refrigerant whose ozone depletion potential is zero and whose global warming potential GWP is small, such as HFO-1123, HFO-1234yf, HFO-1234ze, and HFO-1243zf. “Hydrocarbon” refers to, for example, natural refrigerant such as propane and propylene.
Fluorocarbon-based low-GWP refrigerant such as HFO-1234yf, HFO-1234ze, and HFO-1243zf flows at a refrigerant flow rate of about 2 to 2.5 times the flow rate in a case where HFC-based refrigerant is used. Hence, when the amount of lift of the discharge valve 26 is small, a large pressure loss occurs. In contrast, according to Embodiment 1, the amount of lift can be made large. Consequently, a greater effect is obtained particularly in a case where refrigerant such as HFO-1234yf, HFO-1234ze, and HFO-1243zf is used. The same also applies to a case where hydrocarbon such as propane and propylene, which is natural refrigerant, is used.
Alternatively, a refrigerant mixture containing fluorocarbon-based low-GWP refrigerant such as HFO-1234yf, HFO-1234ze, and HFO-1243zf by 30% or higher may be used. For example, HFC refrigerant whose ozone depletion potential is zero is to be mixed with fluorocarbon-based low-GWP refrigerant. Here, HFC refrigerant refers to, for example, R32, R125, or R161. The same applies to a case where a refrigerant mixture containing HFO-1123 refrigerant by 70% or lower is used. The refrigerant to be mixed with HFO-1123 refrigerant composing 70% or lower of the mixture is “halogenated hydrocarbon containing carbon double bonds” or “HFC refrigerant whose ozone depletion potential is zero” such as R32.
Embodiment 2 differs from Embodiment 1 in that the discharge valve 26 has a helical shape and the valve retainer 27 has a helical shape.
The free end of the discharge valve 26 has a closing portion 26a1, The closing portion 26a1 is shaped to be able to close the discharge port 1f. The closing portion 26a1 has, for example, a shape swelling outward in the widthwise direction of the curved portion 26a. The fixed end of the discharge valve 26 is fixed to the fixed scroll 1 with a bolt 28. The valve retainer 27 is provided above the discharge valve 26.
As illustrated in
Before the fluid flowing in the closed container 20 is compressed in the compression chamber 23, the discharge port 1f is closed by the discharge valve 26 as illustrated in
As described above, the fluid compressor 100 according to Embodiment 2 includes the discharge valve 26 having a helical or substantially helical shape. Consequently, the length of the discharge valve 26 from the fixed end to the free end can be made long. Hence, the curvature can be made large, and the amount of lift can also be made large. Thus, a compact fluid compressor 100 with a reduced pressure loss can be obtained.
Embodiment 3 differs from Embodiment 1 in that the discharge valve 26 includes a curved portion 26a, tongue portions 26b, and a connecting portion 26c and in that the valve retainer 27 has a rectangular shape in plan view.
The curved portion 26a has, for example, an annular shape. The tongue portions 26b project inward from opposite positions on the inner periphery of the curved portion 26a, The connecting portion 26c connects other opposite positions on the inner periphery of the curved portion 26a, The connecting portion 26c extends in the diametrical direction of the curved portion 26a. The connecting portion 26c has a closing portion 26c1 at, for example, the center of the connecting portion 26c. The closing portion 26c1 is shaped to be able to close the discharge port 1f. The closing portion 26c1 has, for example, a shape swelling outward in the widthwise direction of the connecting portion 26c. The closing portion 26c1 is at a position toward which the tongue portions 26b project. The positions on the inner periphery of the curved portion 26a where the tongue portions 26b are provided are different by, for example, 90 degrees to the positions on the inner periphery of the curved portion 26a that are connected by the connecting portion 26c.
The valve retainer 27 is provided over a plane where the discharge port 1f can be closed. The discharge valve 26 and the valve retainer 27 are fixed to the fixed scroll 1 with two bolts 28. When the discharge valve 26 opens the discharge port 1f, the discharge valve 26 is lifted up to the bottom surface of the valve retainer 27.
As illustrated in
Before the fluid flowing in the closed container 20 is compressed in the compression chamber 23, the discharge port 1f is closed by the discharge valve 26 as illustrated in
As described above, the fluid compressor 100 according to Embodiment 3 includes the discharge valve 26 including the curved portion 26a, the tongue portions 26b, and the connecting portion 26c. Consequently, the length from each of the tongue portions 26b to the closing portion 26c1 can be made long. Hence, the curvature of the discharge valve 26 can be made large, and the amount of lift of the discharge valve 26 can also be made large. Thus, a compact fluid compressor 100 with a reduced pressure loss can be obtained. Furthermore, since the discharge valve 26 and the valve retainer 27 are fixed to the compression mechanism with the two bolts 28, the positioning work is not necessary in fastening the bolts 28. Consequently, the valve retainer 27 only needs to control the amount of lift of the closing portion 26c1. The discharge valve 26 can bend in various directions, thus the amount of lift of the discharge valve 26 can be increased without reducing the curvature of the discharge valve 26.
Embodiment 4 differs from Embodiment 1 in that the discharge valve 26 includes a curved portion 26a and a tongue portion 26b and in that the valve retainer 27 has a rectangular shape.
The curved portion 26a has, for example, an annular shape. The curved portion 26a includes a closing portion 26a1 that closes the discharge port 1f. The tongue portion 26b projects inward from the position on the inner periphery of the curved portion 26a opposed to the closing portion 26a1. The tongue portion 26b has, at the tip of the tongue portion 26b, a part that is fixed with a bolt 28. The closing portion 26a1 is at a position toward which the tongue portion 26b projects. The closing portion 26a1 has a shape swelling inward and outward from the curved portion 26a.
The valve retainer 27 has a rectangular shape in plan view and is provided over a plane where the discharge port 1f can be closed. The discharge valve 26 and the valve retainer 27 are fixed to, for example, the fixed scroll 1 with the bolt 28. When the discharge valve 26 opens the discharge port 1f, the discharge valve 26 warps along the valve retainer 27 and is lifted up to the bottom surface of the valve retainer 27.
As illustrated in
Before the fluid flowing in the closed container 20 is compressed in the compression chamber 23, the discharge port 1f is closed by the discharge valve 26 as illustrated in
As described above, the fluid compressor 100 according to Embodiment 4 includes the discharge valve 26 including the curved portion 26a and the tongue portion 26b. Consequently, the length from the tongue portion 26b to the closing portion 26a1 can be made long. Thus, a compact fluid compressor 100 with a reduced pressure loss can be obtained. Furthermore, since the discharge valve 26 has a line-symmetrical shape to the curvature direction, the discharge valve 26 is not twisted when the discharge valve 26 is lifted. Thus, the increase in the stress due to torsion can be minimized. Furthermore, since the discharge valve 26 has an axially symmetrical shape to a line passing through the widthwise center of the tongue portion 26b, the position of the discharge valve 26 when the discharge valve 26 is lifted is laterally balanced. Consequently, the instability due to torsion can be eliminated, and design in consideration of torsional rigidity is unnecessary. Furthermore, since the discharge valve 26 and the valve retainer 27 are fixed to the fixed scroll 1 with one bolt 28, the number of components and thus the manufacturing costs can be reduced.
Furthermore, the present invention is also applicable to a fluid compressor in which a fluid compressed in a compression chamber is discharged to the lower side of the compression chamber. In this case, the discharge valve and the valve retainer are provided at the bottom of the fluid compressor so that the amount of fluid to be discharged from the compression chamber is limited as in the present invention. In such a configuration, a compact fluid compressor with reduced pressure loss at the discharge valve can be obtained as in the present invention.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2014/067577 | 7/1/2014 | WO | 00 |
