JP4271818B2 - Hermetic compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hermetic compressor such as a reciprocating type or a rotary type that encloses and stores an electric element and a compression element in a container.
[0002]
[Prior art]
The structure of a conventional reciprocating hermetic compressor will be described with reference to FIG.
A crankshaft 7 is supported in a sealed container 1 that stores lubricating oil at the bottom, and an electric element 2 composed of a stator 2a and a rotor 2b, and a compression element composed of a cylinder 3, a piston 4, a cylinder head 5, and a head cover 6. A compressor main body is configured by being arranged above and below a frame 8 having a bearing, and the compressor main body is supported by a spring 9 so as to be housed in the hermetic container 1, and the electric element 2 is controlled by an inverter. The rotation speed is changed with.
[0003]
FIG. 7 shows a valve structure used in such a hermetic compressor.
10 is a suction valve, 11 is a suction port, 12 is a discharge port, 13 is a discharge valve, 14 is a valve retainer, 15 is a retainer, 16 is a discharge chamber provided in the head cover 6, and 17 is a compression chamber. The suction valve 10 has a structure in which one end is clamped and fixed between the cylinder head 5 and the cylinder 3, and the other end is seated on a suction port 11 provided in the cylinder head 5, and the suction port 11 is opened and closed by suction gas. ing. Further, the discharge valve 13 is nipped and fixed between the head cover 6 and the cylinder head 5 with one end attached to the retainer 15 together with the valve presser 14, and the other end seated on the discharge port 12 provided in the cylinder head 5. The discharge port 12 is opened and closed by the discharge gas pressure.
In the suction stroke in which the piston 4 moves to the bottom dead center, the discharge valve 13 is closed under the high pressure gas pressure in the discharge chamber 16, and low pressure gas is sucked from the suction port 11, and the suction valve 10 is sucked by the gas pressure. Opens and gas is sucked into the compression chamber 17. When the piston 4 starts to compress from the bottom dead center toward the top dead center, the suction valve 10 is closed, the compression chamber 17 becomes a sealed space, and the gas in the compression chamber 17 is compressed to increase the pressure. After the gas pressure in the compression chamber 17 reaches the pressure in the discharge chamber 16, the discharge valve 13 is opened and the high-pressure gas in the compression chamber 17 is discharged to the discharge chamber 16. When the discharge valve 13 is opened, it comes into contact with the valve presser 14, and the discharge valve 13 pushes up the valve presser 14 and presses the valve presser 14 against the retainer 15. At this time, the valve presser 14 serves as a cushion for reducing the collision of the discharge valve 13 with the retainer 15.
[0004]
[Problems to be solved by the invention]
In the conventional hermetic compressor configured as described above, as shown in FIG. 8, when the refrigerant gas is sucked from the suction port 11, the refrigerant gas pushes up the suction valve 10 to perform suction. In the structure, when the suction valve 10 is opened, self-excited vibration accompanying the flow rate of the refrigerant gas is generated in the suction valve 10, and no consideration is given to the generation of noise due to this self-excited vibration. Further, when the suction valve 10 is seated on the suction port 11, no consideration has been given to the occurrence of noise due to a collision. Such self-excited vibration occurs more significantly during low-speed operation of the compressor where the flow rate of the refrigerant gas is slow.
[0005]
Similarly, when the refrigerant gas is discharged from the discharge port 12, the refrigerant gas pushes up the discharge valve 13 and discharges. However, in the conventional discharge valve structure, when the discharge valve 13 is opened, the refrigerant gas automatically flows with the flow rate of the refrigerant gas. Excited vibration is generated in the discharge valve 13, and noise is generated by the self-excited vibration. Further, when the discharge valve 13 is seated on the discharge port 12, no consideration has been given to the occurrence of noise due to a collision. Such self-excited vibration occurs more significantly during low-speed operation of the compressor where the flow rate of the refrigerant gas is slow.
[0006]
JP-A-57-181981 can be cited as a prior art related to the valve structure.
[0007]
In view of the above, the object of the present invention is to eliminate noise generated by self-excited vibration of the suction valve and the discharge valve, and collision noise generated when sitting on the suction port or the discharge port when the suction valve and the discharge valve are closed. An object of the present invention is to provide a hermetic compressor capable of reducing the above.
[0008]
[Means for Solving the Problems]
A hermetic compressor according to the present invention includes a compression element, an electric element, a suction port into which gas is sucked, and a suction valve that opens and closes in the suction port. A plurality of sheets are stacked, one end of the stacked suction valve is fixed, the other end is seated on the suction port, a through hole is provided in the portion of the suction valve facing the suction port, and the through hole is the suction port In this diameter, the valve tip side is the apex and the valve fixing side is the bottom.
A hermetic compressor according to the present invention is a compressor having a compression element, an electric element, a discharge port from which gas is discharged, and a discharge valve that opens and closes in the discharge port. A plurality of sheets are stacked, one end of the stacked discharge valve is fixed, the other end is seated on the discharge port, a through hole is provided in the discharge valve in a portion facing the discharge port, and the through hole is formed on the discharge port. In this diameter, the valve tip side is the apex and the valve fixing side is the bottom.
A hermetic compressor according to the present invention includes a compression element, an electric element, a suction port through which gas is sucked, a discharge port through which gas is discharged, and a suction port that opens and closes in the suction port or the discharge port. In a compressor having a valve and a discharge valve, a plurality of the suction valves and the discharge valves are stacked, one end of the stacked suction valve and the discharge valve is fixed, and the other end is connected to the suction port or the discharge port A through hole is provided in the suction valve and the discharge valve in a portion facing the suction port or the discharge port, and the through hole is within the diameter of the suction port or the discharge port, and the valve tip side is the apex. And it is set as the structure which is a triangular shape by which a valve fixing side becomes a base.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is an enlarged sectional view of a main part of an embodiment of a hermetic electric compressor according to the present invention, FIG. 2 is an enlarged view of a suction valve, and FIG. 3 is an operation explanatory view of the suction valve.
In the figure, 3 is a cylinder, 4 is a piston, 5 is a cylinder head, and 6 is a head cover that constitutes a compression element. Reference numeral 11 denotes a suction port, 12 denotes a discharge port, 14 denotes a valve presser, 15 denotes a retainer, and 16 denotes a discharge chamber provided in the head cover 6. Reference numeral 17 denotes a compression chamber, 18 denotes a first suction valve, 19 denotes a second suction valve, 20 denotes a first discharge valve, and 21 denotes a second discharge valve.
[0010]
As shown in FIG. 1 and FIG. 2, the suction port 11 is provided with two suction valves, a first suction valve 18 and a second suction valve 19, and the first suction valve 18 seals the suction port 11 on the surface. The area is 80% or less with respect to the area of the suction port 11 and has a structure in which a through hole 18a is provided eccentric to the distal end side of the valve moving portion of the first suction valve 18 (the broken line indicates the suction port 11). Indicates size). Further, the shape of the vicinity of the fixed portion of the first suction valve 18 and the vicinity of the fixed portion of the second suction valve 19 are different (in this embodiment, the through hole 19a is formed in the second suction valve 19), and the spring constant is Both have different structures (first suction valve <second suction valve). Reference numerals 18 b and 19 b denote through holes formed at positions corresponding to the discharge ports 12.
That is, the first suction valve 18 is provided with a through hole 18a, and the two suction valves 18 and 19 are overlapped to seal the suction port 11, so that the suction valves 18 and 19 are opened from the suction port 11. The force due to the gas pressure acts on the first suction valve 18 by a force obtained by subtracting the area of the through hole 18 a from the area of the suction port 11. Further, the second suction valve 19 acts as a force corresponding to the area of the through hole 18a. Furthermore, since the through hole 18 a is provided at the tip of the valve motion part of the first suction valve 18, the gas pressure acts on the tip of the valve motion part of the second suction valve 19. For this reason, the second suction valve 19 has a structure that is easy to open, and the spring constants of the first suction valve 18 and the second suction valve 19 are different. Deviation occurs. Further, the force received from the gas pressure is different while the two suction valves are open, and as shown in FIG. 3, the through hole 18a of the first suction valve 18 on the suction port 11 side receives the suction gas. By disturbing the flow (flow indicated by the solid line arrow), the operation modes of the two suction valves 18 and 19 can be made different.
Further, when the piston 4 reaches the bottom dead center and the first suction valve 18 and the second suction valve 19 are closed, the first suction valve 18 serves as a cushion for the second suction valve 19, so that the second suction valve 19 is Collisions with the cylinder head 5 that occur during closing can be mitigated.
[0011]
Similarly, as shown in FIG. 1, the discharge port 12 is provided with two discharge valves, a first discharge valve 20 and a second discharge valve 21, and the discharge port 12 is provided on the surface where the first discharge valve 20 seals the discharge port 12. The through hole 20a is provided so as to be eccentric to the tip of the valve motion part of the first discharge valve 20 with an area of 80% or less of the area. Further, the shapes of the vicinity of the fixed portion of the first discharge valve 20 and the vicinity of the fixed portion of the second discharge valve 21 are different, and thus the spring constants are different between the two (first discharge valve <second discharge valve). valve).
That is, the first discharge valve 20 is provided with a through hole 20a, and the discharge port 12 is sealed by overlapping the two discharge valves 20 and 21, so that the discharge valves 20 and 21 can be opened from the discharge port 12. The gas pressure force acts on the first discharge valve 20 by a force obtained by subtracting the area of the through hole 20a from the port area. The second discharge valve 21 acts as a force corresponding to the area of the through hole 20a.
Furthermore, since the through hole 20 a is provided at the tip of the valve motion part of the first discharge valve 20, the gas pressure acts on the tip of the valve motion part of the second discharge valve 21. For this reason, the second discharge valve 21 has a structure that is easy to open, and the spring constants of the first discharge valve 20 and the second discharge valve 21 are different. Deviation occurs. Further, the force received from the gas pressure differs while the two discharge valves are open, and the through-hole 20a of the first discharge valve 20 on the discharge port 12 side disturbs the flow of the discharge gas. The operation modes of the discharge valves 20 and 21 can be made different.
Further, when the piston 4 reaches the top dead center and the first discharge valve 20 and the second discharge valve 21 are closed, the first discharge valve 20 serves as a cushion for the second valve 21, so the second discharge valve 21 is closed. The collision with the cylinder head 5 that occurs at the time is mitigated.
[0012]
FIG. 4 is an enlarged view of another embodiment of the suction valve.
As shown in the figure, the through-hole 18b provided in the first suction valve 18 has a tip on the tip end side of the valve in the circle of the discharge port 12 indicated by a broken line, and the base on the side opposite to the tip end away from the tip end portion. Is a through hole that approximates a circular triangular shape. The pressure-receiving surface of the suction gas pressure in the first suction valve 18 is increased, and a larger force is applied to the suction gas pressure on the opposite end side than the tip side of the valve motion part of the second suction valve 19. For this reason, the first suction valve 18 and the second suction valve 19 are both easy to operate.
Similarly, a through hole (not shown) provided in the first discharge valve 20 is a through hole approximated to an irregular triangle shape in which the tip end side of the valve is the apex and the counter tip end side is circular in the circle of the discharge port 12. . Since the pressure-receiving surface of the discharge gas pressure in the first discharge valve 20 is increased, and the suction gas pressure is applied with a greater force on the opposite end side than the tip end side on the valve motion part side of the second discharge valve 21, the first discharge valve 20 The second discharge valve 21 has a structure that is easy to operate.
[0013]
An example of the sound pressure level of the compressor having the valve structure according to the above embodiment is shown in FIG.
In the figure, the vertical axis represents the sound pressure level (dB) and the horizontal axis represents the frequency (Hz). Also, the conventional product is indicated by a white bar graph, and the product according to the present invention is indicated by a hatched bar graph (in the figure, 1.0K means 1000 and OA means overall). As is apparent from the figure, the compressor operating sound pressure level is greatly improved in the high frequency region.
In addition, the area ratio between the circular through holes 18a and 20a and the suction port 11 and the discharge port 12 shown in FIG. 2 is less effective when the area ratio is greater than 80%, and the effect increases as the area ratio decreases. Yes. However, even if the area ratio is too small, the expected effect cannot be obtained.
Note that the suction valve or the discharge valve may be three-layered, and the suction valve or the discharge valve is not limited to the reciprocating type as long as it has a suction port and a discharge port, and may be a hermetic compressor such as a rotary type. Good.
[0014]
As described above, according to the present embodiment, since the suction port is overlapped to seal the suction port, the force generated by the gas pressure for opening the valve from the suction port is applied to the first suction valve. Acts on the force obtained by subtracting the area of the through hole provided in the first suction valve from the port area, acting on the second suction valve as a force corresponding to the area of the through hole provided in the first suction valve, Since the gas pressure acts from the tip of the valve motion part of the second suction valve, the structure is such that the second suction valve is easy to open, and the spring constants of the first suction valve and the second suction valve are different. Therefore, the start of the operation of the two suction valves is shifted, and in addition to this, the force received by the gas pressure is different while the two suction valves are open. This occurs in the two suction valves. Each vibration has a different vibration form Because the vibration of each other can be suppressed self-oscillation interfere with vibration of the other party.
[0015]
Also, since the discharge valve uses two discharge valves to seal the discharge port, the force generated by the gas pressure for opening the valve from the discharge port is the port area for the first discharge valve. Acting on the second discharge valve as a force corresponding to the area of the through hole provided in the first discharge valve, and the second discharge in the force obtained by subtracting the area of the through hole provided in the first discharge valve from Because the gas pressure acts from the tip of the valve motion part of the valve, the second discharge valve 19 is easy to open, and the first discharge valve and the second discharge valve have different spring constants. Deviation occurs in the start of operation of the two discharge valves, and in addition, the force received from the gas pressure is different while the two discharge valves are open, and also occurs in the two discharge valves. Because each vibration has a different vibration form, each other's vibration It is possible to suppress interference to self-excited vibration to.
[0016]
【The invention's effect】
According to the present invention, the noise generated by the self-excited vibration of the suction valve and the discharge valve and the collision sound generated when sitting on the suction port or the discharge port when the suction valve and the discharge valve are closed can be eliminated, and the noise can be reduced. A mold compressor can be provided.
[Brief description of the drawings]
FIG. 1 is an enlarged cross-sectional view of a main part of an embodiment of a hermetic electric compressor according to the present invention.
FIG. 2 is an enlarged view of a suction valve in the embodiment of FIG.
3 is an operation explanatory view of a suction valve in the embodiment of FIG. 1. FIG.
FIG. 4 is an enlarged view of another embodiment of the suction valve.
FIG. 5 is an explanatory diagram of a sound pressure level of a hermetic electric compressor.
FIG. 6 is a cross-sectional view of a conventional compressor.
FIG. 7 is a cross-sectional view of a compression element in a conventional compressor.
FIG. 8 is an explanatory diagram of an operating state of a suction valve in a conventional compressor.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Sealed container 2 ... Electric element, 2a ... Stator, 2b ... Rotor 3 ... Cylinder 4 ... Piston 5 ... Cylinder head 6 ... Head cover 7 ... Crankshaft 8 ... Frame 9 ... Spring 10 ... Suction valve 11 ... Suction port 12 ... Discharge port 13 ... Discharge valve 14 ... Valve retainer 15 ... Retainer 16 ... Discharge chamber 17 ... Compression chamber 18 ... First suction valve, 18a, 18b ... Through hole 19 ... Second suction valve, 19a, 19b ... Through hole 20 ... First discharge valve, 20a ... Through hole 21 ... Second discharge valve

Claims (3)

In a compressor having a compression element, an electric element, a suction port into which gas is sucked, and a suction valve that opens and closes in the suction port.
A plurality of the suction valves are stacked,
Fix one end of this stacked suction valve, seat the other end on the suction port,
Providing a through hole in the suction valve of the portion facing the suction port;
The hermetic compressor, wherein the through hole has a triangular shape within a diameter of the suction port, the valve tip side being a vertex and the valve fixing side being a bottom side. In a compressor having a compression element, an electric element, a discharge port from which gas is discharged, and a discharge valve that opens and closes in the discharge port,
A plurality of the discharge valves,
Fix one end of this overlapped discharge valve, seat the other end on the discharge port,
Providing a through hole in the discharge valve of the portion facing the discharge port;
The hermetic compressor, wherein the through-hole has a triangular shape within a diameter of the discharge port, the valve tip side being a vertex and the valve fixing side being a bottom side. In a compressor having a compression element, an electric element, a suction port through which gas is sucked, a discharge port through which gas is discharged, and a suction valve and a discharge valve that are open and close in the suction port or the discharge port ,
A plurality of each of the suction valve and the discharge valve,
Fix one end of the stacked suction valve and discharge valve, and seat the other end on the suction port or the discharge port,
A through hole is provided in the suction valve and the discharge valve of the portion facing the suction port or the discharge port,
The hermetic compressor according to claim 1, wherein the through hole has a triangular shape within a diameter of the suction port or the discharge port, wherein the valve tip side is the apex and the valve fixing side is the bottom.

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