JP7595605B2 - Compressor - Google Patents

Description

The present invention relates to a compressor.

Air conditioners, freezers, and the like are equipped with compressors to compress fluids such as refrigerants. Here, in compressors such as scroll compressors and rotary compressors, which are a type of compressor, a discharge valve mechanism using a reed valve or the like is provided between the compression side where the refrigerant is compressed and the discharge side where the compressed refrigerant is discharged.

For example, in the refrigerant compressor of Patent Document 1, a refrigerant compressed by a compression element on the compression side is discharged from a discharge port equipped with a discharge valve mechanism to the discharge side. In this refrigerant compressor, the discharge port is provided through a main bearing or the like that separates the compression side and the discharge side, and the discharge port can be opened and closed by a valve seat and a valve body provided on the discharge side.
In the refrigerant compressor of Patent Document 1, the valve body of the discharge valve repeatedly comes into contact with the valve seat to open and close, so that the hardness of the valve seat provided on the discharge side of the discharge port is made higher than that of the discharge port to prevent striking wear.

JP 2001-99066 A

However, in conventional compressors with a valve seat on the discharge port, the valve body and valve seat were easily damaged when operating under harsher conditions, such as increasing the pressure difference between the compression side and discharge side or increasing the opening and closing speed. Furthermore, because the valve seat is integrated with other parts, it is not easy to reinforce or replace it. Even if the valve seat is formed in a separate member and pressed in as in Patent Document 1, it is prone to misalignment, floating, deformation, etc. during use, making it difficult to ensure sufficient compression performance.

The present invention has been made to solve the above problems, and aims to provide a compressor that can prevent damage and ensure compression performance even when operated under harsher conditions.

According to a first aspect of the present invention, the compressor includes a base portion separating a compression side from a discharge side, a discharge port penetrating the base portion, a valve body having one end fixed to the base portion and the other end facing the base portion to close the discharge port, and the other end elastically deforming to open the discharge port when the pressure on the compression side becomes greater than the pressure on the discharge side, and a seating plate disposed between the base portion and the valve body and abutting against a surface of the valve body on the side of the base portion to support the valve body, the seating plate being made only of a metal harder than the base portion, and having a through hole corresponding to the discharge port and a through hole formed in the through hole. and fixing portions for the base portion are provided on both sides in the extension direction with respect to the center of the hole, both sides of the seating plate are formed flat, the through hole of the seating plate is formed larger than the discharge opening of the discharge port and is provided so as to surround the discharge opening from the outer periphery, such that the entire area of one of the two sides of the seating plate is in direct contact with the flat surface of the base portion which is larger in area than the one side of the seating plate and is in airtight contact with it, and no other member is interposed between the one side of the seating plate and the surface of the base portion.

According to the present invention, a seating plate made of a material harder than the base is disposed between the base and the valve body, and the surface of the valve body facing the base is supported in contact with the seating plate. Therefore, the valve body does not directly contact the base when opening and closing, and damage to the base can be prevented.
In addition, the seating plate, which is a separate member disposed between the base and the valve body, is fixed to the base by fixing portions on both sides of the seating plate in the extending direction with respect to the center of the through hole corresponding to the discharge port. This makes it easy to attach the seating plate to the base, and also makes it possible to prevent the seating plate from being displaced, floating, deformed, or having a gap with respect to the base due to the pressure of the compressed fluid or vibrations caused when the valve body is opened and closed.

According to a second aspect of the present invention, in the compressor of the first aspect, the seat plate may be fixed to the base portion together with the one end of the valve body in at least one of the fixing portions.
According to this configuration, the seating plate is fixed to the base portion together with one end of the valve body, so that the fixing position and fixing means of the seating plate can be made common to one end of the valve body, thereby simplifying the structure.

According to a third aspect of the compressor of the present invention, in the first or second aspect described above, the through hole of the seating plate may be formed larger than the discharge opening of the discharge port and may be arranged to surround the discharge opening from an outer periphery.
According to this configuration, the through hole of the seating plate is larger than the discharge opening of the discharge port. This makes it possible to prevent even the slightest blockage of the discharge opening of the discharge port by the seating plate due to manufacturing errors in the seating plate, misalignment when the seating plate is attached, or rattle of the seating plate when the compressor is operating, thereby suppressing pressure loss at the discharge opening when the compressed fluid is discharged.

According to a fourth aspect of the compressor of the present invention, in any one of the first to fourth aspects described above, the through hole of the seating plate may be formed smaller than the discharge opening of the discharge port and may be arranged so as to be surrounded by the discharge opening from an outer periphery side.
According to this configuration, the through hole of the seating plate is formed smaller than the discharge opening of the discharge port, so that the opening area on the compression side of the discharge port can be made larger, and the opening area on the discharge side of the discharge port can be made smaller by the seating plate. Therefore, it is easy to ensure a sufficient opening area on the compression side, and pressure loss when introducing compressed fluid into the discharge port can be suppressed. In addition, the use of the seating plate makes it easy to realize a structure in which the opening area changes in two stages in the discharge direction.
Furthermore, since the area blocked by the valve body can be reduced while maintaining a large opening area of the discharge port, when the through hole is closed by the valve body, deformation such as the valve body entering the through hole is less likely to occur, and the sealing performance between the valve body and the area around the through hole can be improved.
Furthermore, by making the through hole in the seating plate smaller, the strength of the seating plate and the valve body can be improved.

According to a fifth aspect of the compressor of the present invention, in any one of the first to fourth aspects, a seal member may be installed between the seating plate and the base portion in an annular shape surrounding the discharge port.
According to this configuration, the sealing member eliminates a gap between the seat plate and the base portion, making it possible to prevent compressed fluid from leaking from between the seat plate and the base portion, and thus making it easier to ensure compression performance.

According to a sixth aspect of the compressor of the present invention, in any one of the first to fifth aspects, the through hole may have a chamfered portion on an edge portion on the valve body side.
According to this configuration, since the through hole has a chamfered portion on the valve body side, it is possible to prevent the valve body from being damaged when the valve body is seated on the seating plate. Furthermore, since the opening area of the discharge port can be gradually increased toward the discharge side, it is possible to reduce the pressure loss of the fluid during discharge.

The compressor of the present invention can prevent damage and ensure compression performance even when operated under harsher conditions.

1 is a vertical cross-sectional view showing a compressor according to a first embodiment of the present invention. 1A and 1B show a discharge valve mechanism according to a first embodiment of the present invention, in which FIG. FIG. 2 is a top view showing a seating plate of the discharge valve mechanism according to the first embodiment of the present invention. FIG. 4 is a vertical cross-sectional view showing a first modified example of the discharge valve mechanism according to the first embodiment of the present invention. FIG. 4 is a vertical cross-sectional view showing a second modified example of the discharge valve mechanism according to the first embodiment of the present invention. FIG. 11 is a vertical cross-sectional view showing a third modified example of the discharge valve mechanism according to the first embodiment of the present invention. FIG. 11 is a vertical cross-sectional view showing a discharge valve mechanism according to a fourth modified example of the first embodiment of the present invention. FIG. 11 is a vertical cross-sectional view showing a fifth modified example of the discharge valve mechanism according to the first embodiment of the present invention. FIG. 13 is a vertical cross-sectional view showing a discharge valve mechanism according to a sixth modified example of the first embodiment of the present invention.

Hereinafter, a compressor A according to an embodiment of the present invention will be described.
Here, in this embodiment, the compressor A will be described as a vertical scroll compressor provided in an air conditioner, a refrigerator, or the like.

As shown in FIG. 1, the compressor A of this embodiment is configured with a housing 1, an electric motor 2 provided within the housing 1, and a scroll compression mechanism 3 also provided within the housing 1, which compresses a fluid such as a refrigerant by being driven by the electric motor 2.

The housing 1 comprises a cylindrical housing body 1a, an upper cover 1b that closes the opening at the upper end of the housing body 1a, and a lower cover 1c that closes the opening at the lower end of the housing body 1a. The housing 1 is provided with a suction pipe 4 on the side of the housing body 1a for supplying a fluid such as a refrigerant from an accumulator (not shown) into the housing 1. In addition, the upper cover 1b is provided with a discharge pipe 5 for discharging the fluid compressed by the scroll compression mechanism 3 to the outside.

The electric motor 2 includes a stator 6 and a rotor 7. When power is supplied to the stator 6 from a power source, the rotor 7 rotates about an axis O1 extending in the vertical direction S1.
A rotating shaft 8 is attached integrally to the rotor 7 with its axis O1 directed in the up-down direction S1. The rotating shaft 8 is journalled at its upper end in the axis O1 direction by an upper bearing 10 and at its lower end by a lower bearing 11 so as to rotate about the axis O1 together with the rotation of the rotor 7. The upper bearing 10 and the lower bearing 11 are each fixed integrally to the housing main body 1a.
An eccentric pin 12 is integrally provided on the upper end of the rotating shaft 8 with its axis O2 directed in the vertical direction S1 and eccentric (offset) with respect to the axis O1 of the rotating shaft 8.

The scroll compression mechanism 3 includes a fixed scroll 15 (base part), a revolving scroll 16 that revolves eccentrically relative to the fixed scroll 15 by the electric motor 2, and a discharge cover 17 (base part).

The fixed scroll 15 has a disk-shaped end plate 15a and a fixed wrap 15b that protrudes downward from the underside of the end plate 15a and is arranged in a spiral shape. The fixed scroll 15 is fixed in the housing 1 by, for example, bolting it to the upper bearing 10.

The orbiting scroll 16 is formed with a disk-shaped end plate 16a and orbiting wraps 16b that protrude upward from the upper surface of the end plate 16a and are arranged in a spiral shape. The orbiting wraps 16b of the orbiting scroll 16 are housed between the fixed wraps 15b of the fixed scroll 15.

Further, a boss 20 is integrally provided on the lower surface of the end plate 16a of the orbiting scroll 16, and the eccentric pin 12 is fitted into the boss 20.
As a result, the orbiting scroll 16 is eccentrically connected to the rotating shaft 8, and is provided so as to rotate (revolve) with a radius equal to the eccentric distance from the axis (axial center) O1 of the rotating shaft 8, following the rotation of the rotating shaft 8 about the axis O1. The orbiting scroll 16 revolves without rotating on its own axis.

The fixed scroll 15 and the orbiting scroll 16 have their fixed wraps 15b and orbiting wraps 16b meshed together so that they overlap vertically. The fixed scroll 15 and the orbiting scroll 16 are offset from each other by a predetermined amount, and the fixed wraps 15b and orbiting wraps 16b mesh together with a phase shift of 180 degrees. The fixed wraps 15b and orbiting wraps 16b come into contact with each other at multiple points depending on the rotation angle of the orbiting scroll 16.

Between the bottom surface of the fixed scroll 15 and the top surface of the orbiting scroll 16, i.e., the portion where the fixed wrap 15b and the orbiting wrap 16b are meshed, is a compression chamber 21 that compresses a fluid such as a refrigerant. In the scroll compression mechanism 3 of this embodiment, this compression chamber 21 is formed point-symmetrically with respect to the center of the spiral of the fixed wrap 15b and the orbiting wrap 16b, and is configured to gradually transition toward the inner periphery while decreasing in volume in response to the orbiting motion of the orbiting scroll 16, so that the fluid is maximally compressed at the center of the spiral.

The end plate 15a of the fixed scroll 15 is provided with a discharge port 15c that penetrates the end plate 15a and connects the upper and lower spaces at a position corresponding to the center of the compression chamber 21, and a discharge valve mechanism C is configured on the upper side of the discharge port 15c. The discharge valve mechanism C is a mechanism that opens and closes the discharge opening 15d of the discharge port 15c depending on the pressure difference between the intermediate chamber 19 between the fixed scroll 15 and the discharge cover 17 and the compression chamber 21.

The discharge cover 17 is disposed above the fixed scroll 15 and divides the interior of the housing 1 into a lower space and intermediate chamber 19 to which the suction pipe 4 is connected, and an upper discharge chamber 22 to which the discharge pipe 5 is connected.
The discharge cover 17 is provided with a discharge port 17c that penetrates the discharge cover 17 to communicate between the upper and lower spaces, and a discharge valve mechanism B is configured on the upper surface side of the discharge port 17c. The discharge valve mechanism B is a mechanism that opens and closes a discharge opening 17d of the discharge port 17c in response to the pressure difference between the intermediate chamber 19 and the discharge chamber 22.

As shown in Figs. 2(a) and 2(b), the discharge valve mechanism B and the discharge valve mechanism C include discharge ports 15c, 17c penetrating the end plate 15a of the fixed scroll 15 or the discharge cover 17, valve seats 15e, 17e provided on the upper surface of the end plate 15a of the fixed scroll 15 or the discharge cover 17, a valve body 25 that faces and closes the discharge ports 15d, 17d of the discharge ports 15c, 17c, a seat plate 28 arranged between the end plate 15a of the fixed scroll 15 or the discharge cover 17 and the valve body 25, and a retainer 26 arranged to overlap the valve body 25 and the discharge port 17d.

The valve seats 15e, 17e are formed directly on the upper surface of the end plate 15a of the fixed scroll 15 and the upper surface of the discharge cover 17. The valve seats 15e, 17e each have a surface shape that corresponds to the surface shape of the opposing valve body 25, and in this embodiment, are formed in a flat shape over substantially the entire area that faces the valve body 25. The end plate 15a, the valve seat 15e, the discharge cover 17, and the valve seat 17e are made of, for example, cast iron.

The valve body 25 is formed of, for example, a stainless steel reed valve, and one end 25a is fixed to the end plate 15a of the fixed scroll 15 or the upper surface of the discharge cover 17. The other end 25b is in opposing contact with the valve seats 15e, 17e to close the discharge ports 15c, 17c.
The valve body 25 is formed so as to be elastically deformable with one end 25 a fixed to the end plate 15 a of the fixed scroll 15 or the upper surface of the discharge cover 17 as a fulcrum.

The seat plate 28 is made of a material such as metal (e.g., carbon tool steel (SK material)) that is harder than the end plate 15a of the fixed scroll 15 or the discharge cover 17. Both sides of the seat plate 28 are formed flat, one side abuts against and supports one surface of the valve body 25, and the other side abuts against the valve seats 15e, 17e in airtight contact.

As shown in FIG. 3, the seat plate 28 has a through hole 28a corresponding to the discharge ports 15c, 17c, and a plurality of fixing portions 28b, 28c for the end plate 15a of the fixed scroll 15 or the discharge cover 17 provided at positions on both sides of the center of the through hole 28a. The fixing portions 28b, 28c are holes that pass through the seat plate 28.

In detail, the center position P1 of one of the fixing parts 28b is disposed on the opposite side of the center P3 across a straight line O4 that passes through the center P2 of the through hole 28a and is perpendicular to a line O3 that connects the center P3 of the other fixing part 28c and the center P2 of the through hole 28a. That is, the fixing parts 28b and 28c are disposed on both sides of the center P2 of the through hole 28a in the extending direction of the seating plate 28. Furthermore, the center P2 of the through hole 28a and the center P3 of the fixing part 28c of the seating plate 28 are disposed in a straight line on the line O3, and the center position P1 of the fixing part 28b is not disposed on the line O3. As a result, the seating plate 28 is L-shaped when viewed from above.
In this embodiment, one of the fixed portions 28 c is fixed to one end 25 a of the valve body 25 and to the end plate 15 a of the fixed scroll 15 or the discharge cover 17 .

In this embodiment, as shown in FIG. 4, the through hole 28a of the seat plate 28 may be formed larger than the discharge ports 15d and 17d of the discharge ports 15c and 17c, although this is not particularly limited. The through hole 28a and the discharge ports 15d and 17d are arranged concentrically, and the through hole 28a is formed slightly larger than the discharge ports 15d and 17d so that the through hole 28a surrounds the discharge ports 15d and 17d from the outer periphery.

In addition, in this embodiment, as shown in FIG. 5, a chamfered portion 28e may be provided on the edge of the through hole 28a on the valve body 25 side. The chamfered portion 28e is a surface that slopes radially inward of the through hole 28a as it approaches the end plate 15a or the discharge cover 17. In the example of FIG. 5, the chamfered portion 28e is formed from the edge of the through hole 28a on the valve body 25 side to a midpoint in the extension direction of the through hole 28a. The chamfered portion 28e may be formed by machining the edge of the through hole 28a, or the press sag formed when punching the through hole 28a may be used as the chamfered portion 28e.

In addition, in this embodiment, as shown in FIG. 6, a seal member 28d may be attached between the seat plate 28 and the end plate 15a of the fixed scroll 15 or the discharge cover 17, surrounding the discharge ports 15c, 17c in an annular shape. The seal member 28d is a gasket, an O-ring, or the like.

The retainer 26 has one end fixed to and supported by the discharge cover 17 and is inclined upward toward the other end so as to overlap the valve body 25 and the discharge port 17d. The retainer 26 is inclined from one end to the other end to regulate the lift amount at each position when the valve body 25 is lifted up due to elastic deformation caused by a pressure difference.
In this embodiment, the seat plate 28, the valve body 25, and the retainer 26 are fastened together to the end plate 15a of the fixed scroll 15 or the discharge cover 17 at the same position on one side.

In the compressor A described above, when the orbiting scroll 16 revolves by rotating at an eccentric position relative to the fixed scroll 15 due to the electric motor 2, the refrigerant is compressed in the compression chamber 21 between the spiral-shaped fixed wrap 15b and the orbiting wrap 16b, and is compressed to its maximum at the center of the spiral.
In the discharge valve mechanism B, when the pressure of the compression chamber 21 is equal to or lower than the pressure of the intermediate chamber 19, the other end 25b is kept in a state in which the discharge port 17d is closed. When the pressure of the compression chamber 21 becomes greater than the pressure of the intermediate chamber 19, the fixed portion on the one end 25a serves as a fulcrum and elastically deforms in response to the pressure difference, causing the other end 25b to lift up from the valve seat 15e and the seating plate 28 and open the discharge port 17d. This allows the compressed fluid to be fed from the compression chamber 21 to the intermediate chamber 19 through the discharge port 17d. When the pressure of the compression chamber 21 becomes equal to or lower than the pressure of the intermediate chamber 19, the other end 25b of the valve body 25 returns to its original state and closes the discharge port 17d.

In the discharge valve mechanism C, when the pressure in the intermediate chamber 19 is equal to or lower than the pressure in the discharge chamber 22, the other end 25b is kept in a state in which the discharge port 17d is closed. When the pressure in the intermediate chamber 19 becomes greater than the pressure in the discharge chamber 22, the fixed portion on the one end 25a serves as a fulcrum and elastically deforms in response to the pressure difference, causing the other end 25b to lift up from the valve seat 15e and the seating plate 28 and open the discharge port 17d. This allows the compressed fluid to be fed from the intermediate chamber 19 to the discharge chamber 22 through the discharge port 17d. When the pressure in the compression chamber 21 becomes equal to or lower than the pressure in the intermediate chamber 19, the other end 25b of the valve body 25 returns to its original state and closes the discharge port 17d.
As these operations are continued, the compressed fluid is sequentially discharged from the discharge pipe 5 for use.

According to the compressor A described above, a seat plate 28 made of a harder material than the end plate 15a or discharge cover 17 of the fixed scroll 15 is disposed between the end plate 15a or discharge cover 17 of the fixed scroll 15 and the valve body 25, and one side surface of the valve body 25 is abutted and supported. Therefore, the valve body 25 does not directly abut against the end plate 15a or discharge cover 17 of the fixed scroll 15 when opening or closing. This reliably prevents the valve seats 15e, 17e provided on the end plate 15a or discharge cover 17 of the fixed scroll 15 from being damaged by the impact when the valve body 25 is opened or closed.

In addition, a seating plate 28, which is a separate member arranged between the end plate 15a of the fixed scroll 15 or the discharge cover 17 and the valve body 25, is fixed to the end plate 15a of the fixed scroll 15 or the discharge cover 17 by a plurality of fixing portions 28b, 28c provided at both sides in the extending direction of the seating plate 28, sandwiching the center P2 of the through hole 28a corresponding to the discharge ports 15c, 17c. Therefore, the seating plate 28 can be easily attached to the end plate 15a of the fixed scroll 15 or the discharge cover 17. Furthermore, it is possible to prevent the seating plate 28 from being displaced, floating, deformed, having a gap, or the like with respect to the valve seats 15e, 17e due to the pressure of the compressed fluid discharged from the discharge ports 15c, 17c, vibrations when the valve body 25 is opened and closed, and the like.
Therefore, the compression performance of the compressor A can be easily ensured even under severe operating conditions (such as operating conditions with a high rotation speed) while preventing damage to the valve seats 15e, 17e.

In addition, in the compressor A of this embodiment, the seat plate 28 is fixed to the end plate 15a of the fixed scroll 15 or the discharge cover 17 together with one end 25a of the valve body 25 at one of the fixed portions 28b, so the fixing position and fixing means of the seat plate 28 can be made common to the one end 25a of the valve body 25, simplifying the structure.

In addition, in the compressor A of this embodiment, the through hole 28a of the seat plate 28 may be formed larger than the discharge ports 15d, 17d of the discharge ports 15c, 17c, as shown in Figure 4. In this case, it is possible to prevent the discharge ports 15d, 17d of the discharge ports 15c, 17c from being blocked even slightly by the seat plate 28 due to manufacturing errors in the seat plate 28, misalignment when the seat plate 28 is attached, or backlash of the seat plate 28 during operation of the compressor A, and it is possible to suppress pressure loss at the discharge ports 15d, 17d when the compressed fluid is discharged.

In addition, in the compressor A of this embodiment, as shown in FIG. 5, the seating plate 28 may be provided with a chamfered portion 28e. In this case, when the valve body 25 seats on the seating plate 28, it is possible to prevent the valve body 25 from being damaged. Furthermore, since the opening area of the discharge ports 15d, 17d can be gradually increased toward the discharge side, the pressure loss of the fluid during discharge can be reduced.

In addition, in the compressor A of this embodiment, as shown in FIG. 6, a seal member 28d may be attached between the seat plate 28 and the end plate 15a of the fixed scroll 15 or the discharge cover 17, surrounding the discharge ports 15c, 17c in an annular shape. In this case, it is possible to prevent compressed fluid from leaking between the seat plate 28 and the end plate 15a of the fixed scroll 15 or the discharge cover 17, making it easier to ensure the compression performance of the compressor A.

Although the embodiment of the present invention has been described in detail above with reference to the drawings, the specific configuration is not limited to this embodiment, and design changes and the like that do not deviate from the gist of the present invention are also included.
7, the end plate 15a or the discharge cover 17 may have recesses 15f, 17f formed therein that correspond to the shape of the seating plate 28 and have a depth equal to the thickness of the seating plate 28. The seating plate 28 fits into the recesses 15f, 17f. In this case, the positional deviation of the seating plate 28 with respect to the end plate 15a or the discharge cover 17 can be further prevented.

Also, as shown in FIG. 8, the through hole 28a of the seating plate 28 may be formed smaller than the discharge ports 15d, 17d of the discharge ports 15c, 17c. The through hole 28a and the discharge ports 15d, 17d are arranged coaxially, and the through hole 28a is arranged so as to be surrounded from the outer periphery by the discharge ports 15d, 17d. In this case, since the through hole 28a of the seating plate 28 is formed smaller than the discharge ports 15d, 17d, the opening area can be increased on the compression side of the discharge ports 15c, 17c, and the opening area can be reduced by the seating plate 28 on the discharge side of the discharge port. Therefore, it is easy to secure a sufficient opening area on the compression side, and pressure loss when introducing compressed fluid into the discharge ports 15c, 17c can be suppressed. In addition, a structure in which such an opening area changes in two stages in the discharge direction can be easily realized by using the seating plate 28. Furthermore, since the area blocked by the valve body 25 can be reduced while the opening area of the discharge ports 15c and 17c on the compression side is kept large, when the through hole 28a is closed by the valve body 25, the valve body 25 is less likely to deform into the through hole 28a, improving the sealing between the valve body 25 and the periphery of the through hole 28a. Also, by making the through hole 28a of the seat plate 28 smaller, the strength of the seat plate 28 and the valve body 25 can be improved.

As shown in FIG. 9, the centers P1, P2, and P3 of the seat plate 38 are aligned in a straight line, and the seat plate 38 may be linear rather than L-shaped. In other words, the shape of the seat plate is not particularly limited, and it is sufficient that fixing parts are provided on both sides of the center P2 of the through hole 28a in the extension direction of the seat plate.

In addition, although the above describes an example in which the various hole shapes of the discharge ports 15c, 17c, etc. are formed in a circular shape, this is not particularly limited and they may be long holes, elliptical holes, square holes, etc.

In addition, it is not necessary to apply the configuration of the above embodiment to both the discharge valve mechanism B and the discharge valve mechanism C, but the configuration of the above embodiment may be applied to at least one of them.

In addition, although compressor A has been described above as a scroll compressor, the above configurations may also be applied to rotary compressors or other compressors.

Reference Signs List 1 Housing 1a Housing body 1b Upper cover 1c Lower cover 2 Electric motor 3 Scroll compression mechanism 4 Suction pipe 5 Discharge pipe 6 Stator 7 Rotor 8 Rotating shaft 10 Upper bearing 11 Lower bearing 12 Eccentric pin 15 Fixed scroll (base portion)
15a End plate 15b Fixed wrap 15c Discharge port 15d Discharge port 15e Valve seat 15f Recess 16 Orbiting scroll 16a End plate 16b Orbiting wrap 17 Discharge cover (base portion)
17c Discharge port 17d Discharge port 17e Valve seat 17f Recess 19 Intermediate chamber 20 Boss 21 Compression chamber 22 Discharge chamber 25 Valve body 25a One end 25b Other end 26 Retainer 28 Seat plate 28a Through hole 28b Fixed portion 28c Fixed portion 28d Seal member 28e Chamfered portion 38 Seat plate A Compressors B, C Discharge valve mechanism O1 Axis O2 Axis O3 Line connecting centers O4 Orthogonal line S1 Up-down direction P1 Center of one fixed portion P2 Center of through hole P3 Center of the other fixed portion

Claims (4)

A base portion that separates the compression side and the discharge side;
a discharge port extending through the base;
a valve body having one end fixed to the base portion and the other end facing the base portion to close the discharge port, and the other end elastically deforms to open the discharge port when the pressure on the compression side becomes greater than the pressure on the discharge side;
a seating plate disposed between the base portion and the valve body and abutting against a surface of the valve body on the side of the base portion to support the valve body,
the seating plate is made only of a metal harder than the base portion, and has a through hole corresponding to the discharge port, and a plurality of fixing portions for fixing to the base portion provided at positions on both sides in an extension direction with respect to a center of the through hole,
Both surfaces of the seat plate are formed flat,
the through hole of the seating plate is formed larger than the discharge opening of the discharge port and is provided so as to surround the discharge opening from an outer periphery, so that an entire area of one of the two surfaces of the seating plate is in direct contact with and airtightly adhered to a planar surface of the base portion having an area larger than that of the one surface of the seating plate,
A compressor in which no other member is interposed between one surface of the seat plate and the surface of the base portion. The compressor according to claim 1, wherein the seat plate is fixed to the base portion together with the one end of the valve body in at least one of the fixed portions. The compressor according to claim 1 or 2, wherein a seal member is attached between the seat plate and the base portion, surrounding the discharge port in an annular shape. The compressor according to any one of claims 1 to 3, wherein the through hole has a chamfered edge on the valve body side.

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