JP6945128B2 - Compressor - Google Patents

Description

The present invention relates to a compressor used in an outdoor unit of an air conditioner or a refrigerator.

Patent Document 1 and Patent Document 2 propose to reduce the stress applied to the discharge valve when the discharge port is closed to prevent the discharge valve from being damaged.
In Patent Document 1, a recess is formed on the inner peripheral surface of the discharge port at least at a position closer to the base end side of the discharge valve. Therefore, when the discharge valve is closed, the valve seat is elastically deformed toward the concave portion to absorb the impact.
In Patent Document 2, the strength of the portion where the valve body tip side of the valve seat on which the compressive load acts greatly is seated is made larger than the strength of the portion where the base end side of the valve body on which the compressive load acts is relatively small. Is forming. Therefore, the collapse, buckling, and fatigue of the valve seat can be suppressed, and the deterioration of the compressor performance due to the deterioration of the sealing property can be suppressed.

Japanese Unexamined Patent Publication No. 2014-129996 Japanese Unexamined Patent Publication No. 2012-188934

In Patent Document 1 and Patent Document 2, the durability of the discharge valve is improved by changing the shape of the valve seat.

The present invention provides a compressor capable of reducing the impact force on the valve seating portion when the valve is seated and improving the durability of the valve without changing the specifications of the valve, valve retainer, and discharge port. The purpose is to provide.

The compressor of the present invention according to claim 1 has a compression chamber for compressing a refrigerant, a discharge port for discharging the refrigerant compressed in the compression chamber, a valve for opening and closing the discharge port, and an opening / closing operation range of the valve. The discharge head forming the discharge port is provided with a regulating valve retainer, the discharge port has a valve mounting surface, the discharge port has a port seating portion with which the valve abuts, and the valve mounting surface has the valve. a of the fixed end attached by pressing down at the fixed end side of the valve retainer compressor, the port seat, formed in a ring shape on the discharge side of the discharge port at a certain height, by the valve retainer The position of the valve whose opening direction bending operation of the valve is regulated is defined as a valve holding fulcrum, and the position of the valve whose closing direction bending operation of the valve is regulated by the valve mounting surface is defined as a valve seating fulcrum. When the surface of the valve from the valve seating fulcrum to the valve seating fulcrum on the discharge port side is used as the valve seating surface, the valve is formed by a fixed portion that does not perform the opening direction bending operation by the valve holding fulcrum and the valve seating fulcrum. It is composed of a movable part in which the closing direction bending operation is not regulated and a semi-movable part from the valve holding fulcrum to the valve seating fulcrum. The valve width between the portion excluding the port retainer and the semi-movable portion is narrower than the fixed portion with the valve retainer fulcrum as a boundary to a range of 3.2 mm to 10 mm, and the valve seating from the valve retainer fulcrum. When the length of the valve to the fulcrum is the seating length and the length from the valve holding fulcrum to the center of the port seating portion is the valve movable length, the ratio of the seating length to the valve movable length is defined as the ratio of the seating length to the valve movable length. It is characterized in that it is in the range of 0.15 to 0.5.
The compressor of the present invention according to claim 2 is characterized in that, in the compressor according to claim 1, the dimension between the valve seating surface and the port seating portion is smaller than 0.1 mm.
The compressor of the present invention according to claim 3 is the compressor according to claim 1 or 2, wherein the plate thickness of the valve is in the range of 0.3 mm to 0.5 mm.
The compressor of the present invention according to claim 4 is the compressor according to any one of claims 1 to 3, wherein the valve is made of stainless steel or carbon steel.

According to the present invention, it is possible to reduce the impact force on the port seated portion of the valve when the valve is seated and improve the durability of the valve.

Cross-sectional view of the compressor according to an embodiment of the present invention Plan view and cross-sectional view showing the main bearing of the compressor Plan view and cross-sectional view showing the main components of the compressor

In the compressor according to the first embodiment of the present invention, the port seating portion is formed at a constant height in a ring shape on the discharge side of the discharge port, and the valve pressing regulates the valve opening direction bending operation. The position of is the valve holding fulcrum, the valve position where the valve closing direction bending operation is regulated by the valve mounting surface is the valve seating fulcrum, and the surface on the valve discharge port side from the valve holding fulcrum to the valve seating fulcrum is the valve seating surface. Then, the valve consists of a fixed part that does not bend in the open direction by the valve holding fulcrum, a movable part that does not regulate the closing movement by the valve seating fulcrum, and a semi-movable part from the valve holding fulcrum to the valve seating fulcrum. in the configuration, the valve seating surface, higher than the port seat, the valve width in the region and the semi-moving part except the port pressing portion from the movable portion, is narrower than the fixed portion as a boundary the valve retainer fulcrum, When the range is 3.2 mm to 10 mm, the length of the valve from the valve retainer fulcrum to the valve seating fulcrum is the seating length, and the length from the valve retainer fulcrum to the center of the port seating portion is the valve movable length, the valve is movable. The ratio of the seating length to the length is in the range of 0.15 to 0.5. According to the present embodiment, it is possible to reduce the impact force on the port seated portion of the valve when the valve is seated and improve the durability of the valve. Further, by setting the ratio of the seating length to the movable valve length of the valve in the range of 3.2 mm to 10 mm in the valve width in the range of 0.15 to 0.5, the twist of the valve is suppressed and one-sided contact is performed. Since the seating impact load can be dispersed while avoiding the above, the impact force on the port seating portion of the valve can be relaxed and the durability of the valve can be improved.

A second embodiment of the present invention is a compressor according to the first embodiment in which the dimension between the valve seating surface and the port seating portion is smaller than 0.1 mm. According to this embodiment, the durability of the valve can be improved without causing refrigerant leakage from the discharge port.

The third embodiment of the present invention is the compressor according to the first or second embodiment in which the plate thickness of the valve is in the range of 0.3 mm to 0.5 mm. According to this embodiment, sufficient design strength can be ensured.

In the fourth embodiment of the present invention, the valve is made of stainless steel or carbon steel in the compressor according to any one of the first to third embodiments. According to this embodiment, sufficient design strength can be ensured.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view of the compressor according to the present embodiment.
The compressor according to this embodiment includes an electric motor unit 20 and a compression mechanism unit 30 in a closed container 10. The motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40.
The electric motor unit 20 includes a stator 21 fixed to the inner surface of the closed container 10 and a rotor 22 rotating in the stator 21.

The compressor according to this embodiment has a first compression mechanism unit 30A and a second compression mechanism unit 30B as the compression mechanism unit 30.
The first compression mechanism unit 30A has a first cylinder 31A, a first piston 32A arranged in the first cylinder 31A, and a vane (not shown) for partitioning the inside of the first cylinder 31A, and the first piston. The 32A revolves in the first cylinder 31A to suck in and compress the low-pressure refrigerant gas.
Similar to the first compression mechanism unit 30A, the second compression mechanism unit 30B has a vane (shown) that partitions the second cylinder 31B, the second piston 32B arranged in the second cylinder 31B, and the second cylinder 31B. The second piston 32B revolves in the second cylinder 31B to suck in and compress the low-pressure refrigerant gas.

The main bearing 51 is arranged on one surface of the first cylinder 31A, and the middle plate 52 is arranged on the other surface of the first cylinder 31A.
Further, a middle plate 52 is arranged on one surface of the second cylinder 31B, and an auxiliary bearing 53 is arranged on the other surface of the second cylinder 31B.
That is, the middle plate 52 partitions the first cylinder 31A and the second cylinder 31B. The middle plate 52 has an opening larger than the diameter of the shaft 40.
The shaft 40 includes a spindle portion 41 to which the rotor 22 is attached and supported by the main bearing 51, a first eccentric portion 42 to which the first piston 32A is attached, a second eccentric portion 43 to which the second piston 32B is attached, and an auxiliary bearing. It is composed of a sub-shaft portion 44 supported by 53.
The first eccentric portion 42 and the second eccentric portion 43 are formed with a phase difference of 180 degrees, and a connecting shaft portion 45 is formed between the first eccentric portion 42 and the second eccentric portion 43. ..

The first compression chamber 34A is formed between the main bearing 51 and the middle plate 52, between the inner peripheral surface of the first cylinder 31A and the outer peripheral surface of the first piston 32A. Further, the second compression chamber 34B is formed between the middle plate 52 and the auxiliary bearing 53, between the inner peripheral surface of the second cylinder 31B and the outer peripheral surface of the second piston 32B.
An oil reservoir 11 is formed at the bottom of the closed container 10, and an oil pickup 12 is provided at the lower end of the shaft 40.
Further, although not shown, an oil supply passage is formed inside the shaft 40 in the axial direction, and a communication passage for supplying oil to the sliding surface of the compression mechanism portion 30 is formed in the oil supply passage. ..

The closed container 10 is connected to a first suction pipe 13A and a second suction pipe 13B for introducing the suction refrigerant into the compression mechanism unit 30, and a discharge pipe 14 for discharging the compressed refrigerant.
The first suction pipe 13A is connected to the first compression chamber 34A, and the second suction pipe 13B is connected to the second compression chamber 34B. An accumulator 15 is provided on the upstream side of the first suction pipe 13A and the second suction pipe 13B. The accumulator 15 separates the refrigerant returned from the refrigeration cycle into a liquid refrigerant and a gas refrigerant.

Due to the rotation of the shaft 40, the first piston 32A and the second piston 32B revolve in the first compression chamber 34A and the second compression chamber 34B.
The gas refrigerant sucked into the first compression chamber 34A and the second compression chamber 34B from the first suction pipe 13A and the second suction pipe 13B by the revolving motion of the first piston 32A and the second piston 32B is the first compression chamber 34A. After being compressed in the second compression chamber 34B, the gas is discharged into the closed container 10, the oil is separated while passing through the electric motor unit 20 and rising, and the oil is discharged from the discharge pipe 14 to the outside of the closed container 10.
Further, the oil sucked up from the oil reservoir 11 by the rotation of the shaft 40 is supplied to the compression mechanism portion 30 from the communication passage to lubricate the sliding surface of the compression mechanism portion 30.

FIG. 2A is a plan view showing the main bearing of the compressor according to this embodiment.
FIG. 2B is a cross-sectional view of the main bearing in the AOA line of FIG. 2A.
As shown in FIG. 2B, the main bearing 51 that functions as a discharge head has a discharge port 60 that discharges the refrigerant compressed in the first compression chamber 34A, and a valve mounting surface 70.
As shown in FIG. 2A, the discharge port 60 includes a valve 80 that opens and closes the discharge port 60, and a valve retainer 90 that regulates the opening and closing operation range of the valve 80.
The fixed end side of the valve 80 is pressed against the valve mounting surface 70 by the fixed end side of the valve retainer 90 and mounted with the fastening bolt 100.

FIG. 3 is a plan view and a cross-sectional view showing the main components of the compressor according to the present embodiment.
3 (a) is a plan view of the valve retainer, FIG. 3 (b) is a plan view of the valve, FIG. 3 (c) is a cross-sectional view of a main part of the discharge head, and FIG. 3 (d) is shown in FIG. 3 (c). It is sectional drawing which shows the state which attached the valve and the valve retainer to the discharge head.
As shown in FIGS. 3A and 3D, the valve retainer 90 includes a flat surface portion 92 having a fastening bolt hole 91 on the fixed end side and not bending the valve 80 in the opening direction. It is composed of a curved surface portion 93 that regulates the opening direction bending operation of the valve 80 within a predetermined range. The boundary line between the flat surface portion 92 and the curved surface portion 93 serves as the valve holding fulcrum X.

As shown in FIGS. 3 (c) and 3 (d), the discharge port 60 has a port seating portion 61 with which the valve 80 abuts. The port seating portion 61 is formed on the discharge side of the discharge port 60 in a ring shape at a constant height. A concave surface 71 lower than the valve mounting surface 70 and the port seating portion 61 is formed between the valve mounting surface 70 and the port seating portion 61.
The boundary line between the valve mounting surface 70 and the concave surface 71 is the valve seating fulcrum Y.

As shown in FIGS. 3 (b) and 3 (d), the valve 80 includes a fixing portion 82 having a fastening bolt hole 81 on the fixed end side and not bending in the opening direction by the valve holding fulcrum X. It is composed of a movable portion 83 in which the closing direction bending operation is not regulated by the valve seating fulcrum Y, and a semi-movable portion 84 from the valve pressing fulcrum X to the valve seating fulcrum Y.
The fixed portion 82, the movable portion 83, and the semi-movable portion 84 are not configured by the valve 80 itself, but are formed by the valve retainer 90 and the valve mounting surface 70.
That is, the position of the valve 80 whose opening direction bending operation of the valve 80 is regulated by the valve pressing 90 is the valve holding fulcrum X, and the position of the valve 80 whose closing direction bending operation of the valve 80 is regulated by the valve mounting surface 70. The valve seating fulcrum Y, and the surface of the semi-movable portion 84 on the discharge port 60 side is the valve seating surface 85.

The valve seating surface 85 is higher than the port seating portion 61 by the dimension H.
As a result, the impact force of the valve 80 on the port seating portion 61 when the valve is seated can be alleviated, and the durability of the valve 80 can be improved.
Here, the dimension H between the valve seating surface 85 and the port seating portion 61 is preferably smaller than 0.1 mm. As a result, the durability of the valve 80 can be improved without causing refrigerant leakage from the discharge port 60.
The length of the valve 80 from the valve pressing fulcrum X to the valve seating fulcrum Y on the valve seating surface 85 is defined as the seating length L1, and the length from the valve pressing fulcrum X to the center of the port seating portion 61 is the valve movable length L2. Then, the ratio of the seating length L1 to the valve movable length L2 is set in the range of 0.15 to 0.5.

Further, the valve width W of the valve 80 is set in the range of 3.2 mm to 10 mm. The valve width W is the width of the movable portion 83 excluding the port holding portion 86 and the semi-movable portion 84.
By setting the ratio of the seating length L1 to the valve movable length L2 of the valve 80 in the valve width W of 3.2 mm to 10 mm in the range of 0.15 to 0.5, the twist of the valve 80 is suppressed. Since one-sided contact can be avoided and the seating impact load can be dispersed, the impact force of the valve 80 on the port seating portion 61 can be alleviated and the durability of the valve 80 can be improved.
By using stainless steel or carbon steel for the valve 80 and setting the plate thickness of the valve 80 in the range of 0.3 mm to 0.5 mm, sufficient design strength can be ensured.

The verification results of the present invention are shown below.
In this embodiment, the dimension H between the valve seating surface 85 and the port seating portion 61 is 0.05 mm, the seating length L1 is 3.7 mm, and the ratio of the seating length L1 to the valve movable length L2 is 0.15. And said.
As a comparative example, the dimension H between the valve seating surface 85 and the port seating portion 61 is −0.02 mm, the seating length L1 is 0.7 mm, and the ratio of the seating length L1 to the valve movable length L2 is 0.03. And said.
The valve 80 in this example and the comparative example was made of stainless steel having a plate thickness of 0.4 mm and a valve width of W8.0 mm, and had a lift amount of 3.0 mm.
The evaluation conditions were forced liquid back high-speed, high-compression intermittent operation. In the forced liquid back high-speed high-compression intermittent operation, R410A is used as the refrigerant, the refrigerant is sealed to the level of liquid compression, the high compression condition is 3.6 / 0.5 MPa (G), and the rotation speed is 0 to 110 rpm. The range was set.
As a result of performing under the above conditions, the number of intermittent operations until the valve 80 was destroyed was 130 times in this example, while it was 30 times in the comparative example, and this example is about 4 times as compared with the comparative example. It was twice as durable.

The present invention can be applied to a one-cylinder compressor, and further, it can be applied not only to a rotary compressor but also to a reciprocating compressor and a scroll compressor.

10 Sealed valve 20 Electric part 21 Fixture 22 Rotator 30 Compression mechanism part 31A 1st cylinder 31B 2nd cylinder 32A 1st piston 32B 2nd piston 40 Shaft 41 Main shaft part 42 1st eccentric part 43 2nd eccentric part 44 Sub-shaft Part 51 Main bearing 52 Middle plate 53 Sub-bearing 60 Discharge port 61 Port seating part 70 Valve mounting surface 71 Concave surface 80 Valve 81 Fastening bolt hole 82 Fixed part 83 Movable part 84 Semi-movable part 85 Valve seating surface 86 Port holding part 90 Valve Presser 91 Hole for fastening bolt 92 Flat surface 93 Curved surface 100 Fastening bolt H Dimension L1 Seating length L2 Valve movable length W Valve width W
X valve holding fulcrum Y valve seating fulcrum

Claims (4)

A compression chamber that compresses the refrigerant and
A discharge port that discharges the refrigerant compressed in the compression chamber, and
A valve that opens and closes the discharge port,
It is equipped with a valve retainer that regulates the opening / closing operation range of the valve.
The discharge head forming the discharge port has a valve mounting surface and has a valve mounting surface.
The discharge port has a port seating portion with which the valve abuts.
A compressor that is attached to the valve mounting surface by pressing the fixed end side of the valve with the fixed end side of the valve retainer.
The port seating portion is formed on the discharge side of the discharge port in a ring shape at a constant height.
The position of the valve whose opening direction bending operation of the valve is regulated by the valve pressing is defined as the valve holding fulcrum, and the position of the valve whose closing direction bending operation of the valve is regulated by the valve mounting surface is defined as the valve seating fulcrum.
When the surface of the valve from the valve holding fulcrum to the valve seating fulcrum on the discharge port side is the valve seating surface.
The valve
A fixed portion that does not perform the opening direction bending operation by the valve holding fulcrum, and a fixing portion.
A movable part whose closing direction bending operation is not regulated by the valve seating fulcrum,
It is composed of a semi-movable portion from the valve holding fulcrum to the valve seating fulcrum, and the valve seating surface is made higher than the port seating portion.
Wherein the valve width at the site and the semi-moving part except the port pressing portion from the movable portion, is narrower than the fixing portion as a boundary said valve retainer fulcrum, and the range of 3.2Mm～10mm, the valve retainer fulcrum The length of the valve from the valve seating fulcrum to the valve seating fulcrum is defined as the seating length.
When the length from the valve holding fulcrum to the center of the port seating portion is defined as the valve movable length,
A compressor characterized in that the ratio of the seating length to the movable valve length is in the range of 0.15 to 0.5. The compressor according to claim 1, wherein the dimension between the valve seating surface and the port seating portion is smaller than 0.1 mm. The compressor according to claim 1 or 2, wherein the plate thickness of the valve is in the range of 0.3 mm to 0.5 mm. The compressor according to any one of claims 1 to 3, wherein the valve is made of stainless steel or carbon steel.

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