JP2009138641A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of improving the sealing performance of a valve seat. <P>SOLUTION: A reed valve 83 provided in a valve storage chamber 89 of a scroll type compressor 11 extends along an extension direction X, and is fixed at one end 86 in an extension direction X, and has the other end 87 in the extension direction X provided oppositely to a valve seat 91. An annular groove 92 is formed around the valve seat 91. A small relief groove 93 having a depth dimension smaller than the annular groove 92 is formed overlapping at the one end side in the extension direction X of the annular groove 92. The relief groove 93 is formed at a section at least overlapping with the reed valve 83. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a compressor in which a reed valve is provided at a discharge port.

The first prior art compressor is provided with a reed valve in the discharge port, and a structure in which an annular groove is provided in a valve seat around the discharge port is disclosed as a seal structure of the discharge port (see, for example, Patent Document 1). . Moreover, the structure which makes a valve seat protrude is disclosed as a sealing structure of the 2nd prior art (for example, refer patent document 2). With these configurations, the sealing performance of the valve seat is improved. Further, the third prior art compressor is a scroll compressor having a plurality of discharge ports, and two of the discharge ports are provided with reed valves. (For example, refer to Patent Document 3).
JP-A-6-101644 Japanese Patent Laid-Open No. 2005-120836 JP 2000-97176 A

  In the seal configuration as in the first prior art described above, the seal surface around the discharge port is secured by an annular groove, but the reed valve sealing performance depends on the flatness of the outer periphery of the annular groove. There's a problem.

  Further, in the seal configuration as in the second prior art described above, the seal is secured by providing a relief in a portion other than the seal portion around the discharge port and the reed valve mounting portion. There is a problem that the manufacturing cost increases due to. Further, even when a relief is provided at the material stage, there is a problem that it is necessary to limit the material.

  Further, in the above-described third conventional scroll compressor, when carbon dioxide is used as a refrigerant as a countermeasure against global warming, the differential pressure between the discharge ports becomes large, and the sealing performance of each discharge port is ensured individually. is important.

  Accordingly, the present invention has been made in view of the above-described problems, and an object thereof is to provide a compressor that can improve the sealing performance of a valve seat at a low cost.

  The present invention employs the following technical means in order to achieve the aforementioned object.

The present invention is a compressor that compresses fluid sucked from the outside and discharges the compressed fluid through a discharge port (79),
A valve seat (91) is formed around the opening on the downstream side of the discharge port,
Having a reed valve (83) that closes the discharge port by contacting the valve seat and opens the discharge port by moving away from the valve seat;
The reed valve is provided so as to extend from one end (86) to the other end (87),
One end of the reed valve is fixed at a predetermined fixed position,
The other end of the reed valve is provided facing the valve seat,
An annular groove (92) is formed around the valve seat,
An escape groove (93) that is continuous with one end of the reed valve of the annular groove and has a smaller depth than the annular groove is formed,
The escape groove is a compressor characterized in that it is formed at least in a portion overlapping with the reed valve when viewed from the downstream side in the discharge direction (Z) of the fluid discharged from the discharge port.

  According to the present invention, an annular groove is formed around the valve seat, and a relief groove is formed in a portion overlapping with the reed valve. Therefore, the remaining portion other than the other end of the reed valve is the remaining portion excluding the valve seat. It is possible to prevent contact with the portion. As a result, even if the flatness of the valve seat is not highly accurate, the other end of the reed valve can be densely arranged on the valve seat. Therefore, it is possible to prevent the fluid from being undesirably discharged from the discharge port.

  Further, since the relief groove has a smaller depth than the annular groove, it is possible to reduce a burr generated at a portion where the relief groove and the annular groove are continuous when the relief groove is processed. As a result, removal of burrs can be facilitated, and processing costs can be reduced. Further, since the burr is small, it is possible to prevent the valve seat from being damaged by removing the burr. Therefore, the sealing performance of the valve seat can be improved at low cost.

The present invention also includes a housing (25),
A fixed scroll (35) fixed inside the housing and having a spiral fixed side spiral (49);
A movable scroll (43) formed between the working chamber (33) for compressing the fluid and the fixed-side spiral portion, and a movable scroll (31) rotating with respect to the fixed scroll;
A plurality of discharge ports communicate with the working chamber, and a plurality of discharge ports are provided.

  According to the present invention, a relief groove is formed in a so-called scroll compressor having a plurality of discharge ports. As a result, when a high-pressure fluid is discharged from a plurality of discharge ports like a scroll compressor, even if the valve seats are densely packed, the sealing performance of the valve seats can be ensured.

Furthermore, in the present invention, the discharge port is formed in the wall portion (47),
A reed valve is accommodated in the wall portion, and a valve accommodating chamber (89) that is concave in the opposite direction from the end surface portion on the discharge direction side of the wall portion is formed.

  According to the present invention, while reducing the recompression loss, the deterioration of the surface roughness and flatness of the end milling of the concave valve storage chamber can be absorbed more and the sealing performance can be improved.

  Furthermore, the present invention is characterized in that a groove (94) is further formed which is connected to one end side of the reed valve of the relief groove and has a depth dimension larger than that of the relief groove.

  According to the present invention, since a groove capable of accommodating foreign matter is formed, the foreign matter is accommodated in the foreign matter groove even when the foreign matter has entered the vicinity of the reed valve. This prevents foreign matter from affecting the operation of the reed valve.

  Further, the present invention is characterized in that the fluid discharged from the discharge port is carbon dioxide.

  According to the present invention, the sealing performance of the valve seat can be ensured even when applied to high-pressure carbon dioxide. Therefore, even if the compressor has a small capacity using carbon dioxide and the valve seats are densely packed, the sealing performance of the valve seats can be ensured.

  Furthermore, the present invention is characterized in that the relief groove has a depth dimension of 0.02 mm to 0.7 mm.

  According to the present invention, it is possible to prevent the flatness of the valve seat from being lowered by forming the escape groove by setting the depth dimension of the escape groove.

  In addition, the code | symbol in the bracket | parenthesis of each above-mentioned means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view showing a scroll compressor 11 in the present embodiment. FIG. 2 is an enlarged plan view showing the vicinity of the discharge port formed in the scroll compressor 11. FIG. 3 is a cross-sectional view of FIG. 2 taken along section line III-III. The scroll type compressor 11 of this Embodiment is used for the compressor for hot water heaters. The scroll compressor 11 of this embodiment uses carbon dioxide as a refrigerant, compresses carbon dioxide, and is used in a refrigeration circuit in which the pressure of discharged carbon dioxide exceeds the critical pressure.

  The scroll compressor 11 includes a sealed container 13, an electric motor unit 15, and a compression mechanism unit 17. The scroll compressor 11 is a hermetic electric compressor in which an electric motor unit 15 and a compression mechanism unit 17 are coaxially accommodated in a hermetic container 13.

  The sealed container 13 includes a cylindrical case 13a having a cylindrical shape, and an electric motor side end case 13b and a compression mechanism side end case 13c assembled to both ends of the cylindrical case 13a.

  The electric motor unit 15 includes a stator 19 fixed to the inner peripheral surface of the cylindrical case 13 a and a rotor 23 fixed to a shaft 21 that is rotationally driven by the electric motor unit 15.

  In the cylindrical case 13 a, the shaft 21 is substantially horizontal by a sub-bearing 39 fixed to a disk-like support member 37 provided between the stator 19 and the motor side end case 13 b and the main bearing 27. It is supported.

  The compression mechanism unit 17 includes a main housing 25, a movable scroll 31, and a fixed scroll 35. The main housing 25 is fixed at a position adjacent to the stator 19 in the cylindrical case 13a. The movable scroll 31 revolves by a crank mechanism 51 supported by a main bearing 27 provided in the main housing 25. The fixed scroll 35 is fixed to the cylindrical case 13 a on the side opposite to the stator 19 of the main housing 25, and is disposed to face the movable scroll 31. A working chamber 33 is formed by the movable scroll 31 and the fixed scroll 35.

  The movable scroll 31 includes a movable side plate 41, a movable side spiral 43, a boss portion 45, and a movable scroll back surface 46. The movable side plate 41 is formed in a substantially disc shape. The movable spiral 43 is erected in a spiral shape, for example, an involute curve shape, from one end surface in the thickness direction of the movable plate 41 toward the fixed scroll 35. The boss portion 45 is erected in a cylindrical shape from the end surface opposite to the movable spiral 43 toward the main housing 25 side. The movable scroll back surface 46 is formed on the outer periphery of the boss portion 45 on the main housing side of the movable scroll 31.

  The fixed scroll 35 includes a fixed side plate 47 fixed to the cylindrical case 13a, and a spiral side provided on the end surface of the fixed side plate 47 on the movable scroll 31 side, for example, a fixed side spiral 49 formed by a groove on an involute curve. Prepare. The fixed scroll 35 is fixed inside the main housing 25. The fixed scroll 35 and the main housing 25 are fastened by fastening means such as a bolt 70 from the main housing 25 side.

  Since the scroll compressor 11 uses carbon dioxide as described above, it is designed so that the discharge pressure exceeds the critical pressure of carbon dioxide. Therefore, the tooth heights of the movable side spiral 43 and the fixed side spiral 49 are set lower than those used in a refrigeration circuit such as Freon so as to withstand the high pressure applied to the working chamber 33.

  The main housing 25 has a two-stage cylindrical shape in which the diameter gradually increases from the motor unit 15 side toward the fixed scroll 35 side. The smallest diameter cylinder 25 a close to the motor unit 15 constitutes the main bearing 27. The large-diameter cylinder 25 b constitutes a crank chamber 53 that houses the crank mechanism 51. A flange portion 25 c that extends and extends radially outward from the fixed scroll 35 side of the large-diameter cylinder 25 b constitutes a thrust bearing portion 55 that receives the thrust load of the movable scroll 31.

  The thrust bearing portion 55 is fixed to the inner peripheral surface of the cylindrical case 13a by fixing means such as shrink fitting. The thrust bearing portion 55 is provided with a recess 45a within a range in which the boss portion 45 of the movable scroll 31 turns. Further, the thrust bearing portion 55 is provided with a movable scroll receiving surface 65a and is flush with the fixed scroll receiving surface 65b, thereby simplifying the processing.

  The crank mechanism 51 is configured by an eccentric shaft 57 provided integrally with an end portion of the shaft 21 on the compression mechanism portion 10 side, and a boss portion 45 of the movable scroll 31. The eccentric shaft 57 is provided so as to be eccentric by a predetermined amount from the shaft centers of the main bearing 27 and the sub bearing 39.

  Between the movable side plate outer peripheral portion 59 outside the movable side spiral 43 of the movable side plate 41 of the movable scroll 31 and the fixed side plate outer peripheral portion 61 outside the fixed side spiral 49 of the fixed side plate 47 of the fixed scroll 35, An Oldham coupling 63 is interposed. The Oldham coupling 63 prevents the movable scroll 31 from rotating with respect to the fixed scroll 35. As a result, the movable scroll 31 only revolves with respect to the fixed scroll 35.

  In such a configuration, the compression mechanism portion 17 has a plurality of working chambers 33 formed by the engagement of the movable-side spiral 43 and the fixed-side spiral 49 so that the movable scroll 31 rotates with respect to the fixed scroll 35. And the refrigerant in the working chamber 33 is compressed.

  The thrust bearing portion 55 has a fixed scroll side end surface 65 formed of a single plane on the fixed scroll 35 side. Between the movable scroll 31 and a surface of the fixed scroll side end surface 65 of the thrust bearing portion 55 that faces the movable scroll back surface 46 of the movable scroll 31 (hereinafter sometimes referred to as “movable scroll receiving surface 65a”), An annular wear-resistant ring 67 is interposed.

  The wear-resistant ring 67 is configured to slide the movable scroll back surface 46 while receiving a force that presses the movable scroll 31 from the fixed scroll 35 toward the main housing 25 when the working chamber 33 becomes high pressure.

  A cylindrical cylindrical protrusion 69 that protrudes toward the fixed scroll side end surface 65 of the main housing 25 is formed on the outer peripheral portion of the fixed side plate 47 of the fixed scroll 35. The tip end surface 69a of the cylindrical protrusion 69 is in pressure contact with the outer peripheral portion 65b of the movable scroll receiving surface 65a of the fixed scroll side end surface 65.

  The motor side end case 13b of the hermetic container 13 is provided with a suction pipe 71, and a pipe in the refrigeration circuit is connected to suck the refrigerant. In addition, a first through hole 73 is formed in the disc-shaped support member 37 provided between the motor side end case 13 b and the stator 19, and the sucked refrigerant can flow into the motor unit 15. It is like that. Further, the outer peripheral portion of the thrust bearing portion 55 of the main housing 25 reaches the scroll outer peripheral space 75 between the outer periphery of the movable scroll 31 and the inner periphery of the cylindrical protrusion 69 of the fixed scroll 35 from the electric motor portion 15 side. A second through hole 77 is formed.

  Next, the vicinity of the valve seat 91 will be described with reference to FIGS. 2 and 3. The fixed side plate 47 is a wall portion, and a discharge port 79 that connects the working chamber 33 and the external space is formed in the fixed side plate 47. Specifically, at the center of the fixed-side spiral 49 of the fixed scroll 35, a plurality of, in this embodiment, three discharge ports that penetrate the fixed-side plate 47 from the movable scroll 31 side to the compression mechanism-side end case 13 c side. 79 is formed (see FIG. 2). A valve seat 91 is formed around the opening on the downstream side of the discharge port 79.

  A valve accommodating chamber 89 is provided in a portion of the fixed side plate 47 where the discharge port 79 on the side opposite to the movable scroll 31 of the fixed scroll 35 is formed (see FIG. 1). Therefore, the downstream opening of the discharge port 79 is formed in the valve storage chamber 89, so that the valve seat 91 is formed in the valve storage chamber 89. The valve storage chamber 89 is formed by digging into a concave shape in the direction opposite to the discharge direction Z from the end surface portion of the fixed side plate 47 on the discharge direction Z side. A discharge chamber 81 connected to the valve storage chamber 89 is provided on the opposite side of the valve storage chamber 89 from the movable scroll 31, that is, on the refrigerant discharge direction Z side. As shown in FIG. 1, the valve accommodating chamber 89 is set to have a smaller volume than the discharge chamber 81. In other words, the volume of the discharge port 79 is made as small as possible. The discharge chamber 81 is provided with a discharge pipe 85 that penetrates the cylindrical case 13a and protrudes to the outside.

  A reed valve device 90 is provided in a portion entering the valve storage chamber 89 from the discharge port 79, that is, a bottom surface portion 98 of the valve storage chamber 89, so that the refrigerant discharged into the valve storage chamber 89 does not flow backward. . The reed valve device 90 includes a reed valve 83 and a stopper 96. The reed valve 83 is accommodated in the valve accommodating chamber 89. The reed valve 83 closes the discharge port 79 by contacting the valve seat 91, and opens the discharge port 79 by separating from the valve seat 91. The reed valve 83 is configured to change the discharge port 79 from the closed state to the open state by being displaced in the discharge direction Z when the pressure of the refrigerant discharged from the discharge port 79 in the discharge direction Z acts. The stopper 96 is provided on the discharge direction Z side of the reed valve 83 and regulates the maximum opening degree of the reed valve 83.

  The reed valve device 90 is provided on the bottom surface portion 98 of the valve storage chamber 89. The reed valve 83 has a substantially rectangular shape extending along a predetermined extending direction X, and one end portion 86 in the extending direction X is fixed to a predetermined fixed position by a bolt 97, which is a bottom surface portion 98 in this embodiment. The Therefore, the reed valve 83 extends from the one end portion 86 to the other end portion 87. The other end portion 87 of the reed valve 83 in the extending direction X is displaced along an arc-shaped displacement locus with the one end portion 86 as a base point to open and close the discharge port 79. The reed valve 83 is displaced so that the other end 87 is isolated from the valve seat 91, and when the reed valve 83 comes into contact with the stopper 96 and reaches a position defined as the maximum opening, the discharge port 79 is fully opened. To do.

  The bottom surface 98 of the valve storage chamber 89 is formed so as to be inclined so that the other end 87 is closer to the working chamber 33 than the one end 86 to which the reed valve 83 is fixed. By inclining the bottom surface portion 98 in this way, the dimension of the discharge port 79 in the discharge direction Z is reduced, and the volume of the discharge port 79 is reduced. Since the volume of the discharge port 79 is a so-called dead volume that does not contribute to the compression of the refrigerant in the working chamber 33, the compression efficiency is increased by reducing this volume. Further, since the valve accommodating chamber 89 has a smaller volume than the discharge chamber 81, the pressure of the refrigerant discharged from the discharge port 79 can be prevented from being lost due to re-expansion.

  With such a configuration, the refrigerant sucked from the suction pipe 71 reaches the scroll outer peripheral space 75 through the first through hole 73 and the second through hole 77. The refrigerant reaching the scroll outer peripheral space 75 is sucked from the outer peripheral portions of the movable side spiral 43 and the fixed side spiral 49 and compressed. The refrigerant compressed to a high pressure in the working chamber 33 between the movable scroll 31 and the fixed scroll 35 is pumped to the discharge chamber 81 through the discharge port 79 and the reed valve 83 and the valve storage chamber 89, and is discharged to the discharge pipe 85. And supplied to the refrigerant pipe in the refrigerant circuit.

  Next, the valve seat 91 provided with the reed valve device 90 will be further described with reference to FIGS. Three discharge ports 79 are provided. Each discharge port 79 is arranged along the arrangement direction Y substantially orthogonal to the extending direction X in which the reed valve 83 extends when viewed from the downstream side in the discharge direction Z. The discharge port 79 in the center in the arrangement direction Y is a main port 79a, and the discharge ports 79 on both sides in the arrangement direction Y are sub-ports 79b. The main port 79 a is provided in the vicinity of the center portion of the fixed-side spiral 49 when viewed from the downstream side in the discharge direction Z. Since the pressure of the working chamber 33 is increased toward the center of the fixed-side spiral 49, when only the main port 79 a is opened and the sub-port 79 b is closed, the sub-port 79 b arranged closer to the suction side However, the differential pressure increases. Two subports 79b are provided. Therefore, the sealing performance of the sub port 79b is more important than the main port 79a.

  An annular groove 92, a relief groove 93 and a foreign matter groove 94 are formed in the bottom surface portion 98 of the valve storage chamber 89. In FIG. 2, the escape groove 93 is hatched to facilitate understanding. The annular groove 92 is formed around the valve seat 91 so as to be annular when viewed from the downstream side in the discharge direction Z. For example, when the inner diameter of the discharge port 79 is 1 mm, the depth dimension d1 of the annular groove 92 is set to 0.5 mm. The outer shape of the annular groove 92 is set to 10 mm, for example.

  The escape groove 93 is connected to one end side in the extending direction X of the annular groove 92 and is formed so that the depth dimension δ is smaller than that of the annular groove 92. The escape groove 93 is formed at least in a portion overlapping with the reed valve 83 when viewed from the downstream side in the discharge direction Z. In the present embodiment, the escape groove 93 extends along the arrangement direction Y, and has three annular grooves 92 and one escape groove 93. Are connected. Therefore, the width dimension W1 which is the dimension of the reed valve 83 in the arrangement direction Y is set to be smaller than the dimension of the escape groove 93 in the arrangement direction Y. Further, with respect to the arrangement direction Y, the dimension W2 between the end portions 95 of the annular groove 92 and the escape groove 93 is set to be larger than the width dimension W1 of the reed valve 83.

  The foreign matter groove 94 is connected to one end side in the extending direction X of the escape groove 93 and is formed so that the depth dimension d2 is larger than the escape groove 93. The foreign matter groove 94 is formed so as to accommodate foreign matter. The foreign matter is, for example, metal powder contained in the fluid, deteriorated material in the refrigeration cycle, or the like. The foreign matter groove 94 is formed at least in a portion overlapping with the reed valve 83 when viewed from the downstream side in the discharge direction Z. The foreign matter groove 94 extends in the arrangement direction Y in the present embodiment, and continues to the escape groove 93. The depth dimension d2 of the foreign material groove 94 is set based on the size of the foreign material, for example, 0.3 mm or more.

  Therefore, when the reed valve 83 is in the closed state, one end 86 is fixed, the other end 87 is in contact with the valve seat 91, and the remaining portion is separated from the bottom surface 98 by the three grooves 92 to 94.

  Next, the depth dimension δ of the escape groove 93 will be described. 4 is an enlarged sectional view showing the vicinity of the valve seat 91 in section IV of FIG. FIG. 5 is a graph showing the relationship between the depth dimension δ of the escape groove 93 and the sagging length x. The horizontal axis in FIG. 5 indicates the depth dimension δ of the escape groove 93, and the vertical axis indicates the sagging length x.

  By forming the relief groove 93 so as to be continuous with the annular groove 92, a burr is always generated at the acute angle portion 95 that is an intersection with the annular groove 92 during processing. When this burr is removed by brushing or the like, the adjacent valve seat 91 is also brushed, and sagging occurs in the valve seat 91 necessary for sealing. As shown in FIG. 5, when the depth dimension δ increases, the sagging length x of the sag shown in FIG. 4 also increases. Therefore, it is necessary to set the depth dimension δ of the relief groove 93 within a range where the sagging length x does not become excessive.

  When the refrigerant is carbon dioxide, the inner diameter of the discharge port 79 is smaller than that of other refrigerants and is about 1 mm, so that the sagging length x is surely 0.1 mm or less, based on FIG. It is preferable to set the depth dimension δ of the escape groove 93 to 0.7 mm or less. Further, the depth dimension δ of the relief groove 93 is preferably set to 0.02 mm or more in consideration of tolerance variation. Therefore, the depth dimension of the escape groove 93 is preferably 0.02 mm or more and 0.7 mm or less. By removing the burr by this, it is possible to prevent the flatness of the valve seat 91 from being lowered.

  Next, a processing process for forming the grooves 92 to 94 in the valve seat 91 will be described. First, a foreign material groove 94 and an annular groove 92 are formed on the bottom surface 98 of the flat valve housing chamber 89 by milling. By forming the annular groove 92, a valve seat 91 is formed in the opening on the downstream side of the discharge port 79.

  Next, the relief groove 93 is formed by milling so that the foreign matter groove 94 and the annular groove 92 are continuous. As a result, three grooves 92 to 94 are formed. At this time, as described above, burrs are generated in the acute angle portion 95 that is the intersection of the annular groove 92 and the escape groove 93. Therefore, next, the burr | flash of the acute angle part 95 is removed by a brush process etc.

  The valve seat 91 is also brushed. Since the valve seat 91 is an annular enclave around the axis of the discharge port 79, the brush comes into contact with the valve seat 91 from one axial direction of the discharge port 79 in order to perform brushing. Next, in a state where the brush is in contact with the valve seat 91, the brush seat 91 is brushed by rotating around the axis. Next, after brush processing of the valve seat 91, the brush is again displaced in the other axial direction. Therefore, the polishing bars formed on the valve seat 91 are concentric around the axis of the discharge port 79. Therefore, since the polishing bar is not shaped to extend along the radial direction of the discharge port 79, it is possible to prevent the inner space of the discharge port 79 from communicating with the valve accommodating chamber 89 by the polishing bar. Therefore, the sealing performance of the valve seat 91 can be improved.

  As described above, in the scroll compressor 11 according to the present embodiment, the annular grooves 92 are formed around the valve seats 91 of the plurality of discharge ports 79, and the escape grooves 93 are formed in the portions overlapping the reed valves 83. Therefore, the remaining part other than the other end 87 of the reed valve 83 can be prevented from contacting the remaining part except the valve seat 91. As a result, even if the flatness of the valve seat 91 is not highly accurate, the other end of the reed valve 83 can be densely disposed in the discharge port 79. Therefore, it is possible to prevent the fluid from being undesirably discharged from the discharge port 79.

  Further, since the relief groove 93 has a depth dimension δ smaller than that of the annular groove 92, it is possible to easily remove burrs generated in the portion 95 where the relief groove 93 and the annular groove 92 are connected when the relief groove 93 is processed. As a result, the processing cost can be reduced. Therefore, the sealing performance of the valve seat 91 can be improved at a low cost.

  Further, when the valve seat 91 is provided on the end surface portion on the discharge direction Z side of the fixed side plate 47, the surface roughness and flatness of the end surface portion are improved by polishing, but the dead volume of the discharge port is reduced and high efficiency is achieved. As described above, the valve housing chamber 82 dug into the concave shape from the fixed side plate 47 is formed. Since the processing for forming such a valve accommodating chamber 82 is limited to end milling, the surface roughness and flatness of the valve seat are deteriorated as compared with the polishing processing. Therefore, when the valve accommodating chamber 82 is formed, the effect of improving the sealing performance of the valve seat 91 by forming the relief groove 93 can be further exhibited.

  Moreover, in this Embodiment, since it has the above effects, even if it is a case where it applies to a high pressure carbon dioxide, the sealing performance of the valve seat 91 is securable. Therefore, even if the compressor 11 has a small capacity using carbon dioxide and the valve seats 91 are densely packed, the sealing performance of the valve seat 91 can be ensured.

  Further, in the present embodiment, since the foreign matter groove 94 is formed, the foreign matter is accommodated in the foreign matter groove 94 even when the foreign matter has entered the vicinity of the reed valve 83. As a result, it is possible to prevent the foreign matter from affecting the operation of the reed valve 83 by the foreign matter biting into one end of the reed valve 83.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In the above-described embodiment, the configuration in the vicinity of the discharge port is realized by the scroll compressor. However, the present invention is not limited to the scroll compressor, and other compressors such as vane type, crank type and swash plate type compressors are used. You may apply to the discharge port of a machine.

  In the above-described embodiment, the present invention is applied to the refrigeration circuit, but is not limited to the refrigeration circuit, and may be used for other purposes. The fluid to be compressed is carbon dioxide, which is a refrigerant. However, the fluid is not limited to this and may be another fluid.

1 is a longitudinal sectional view showing a scroll compressor 11. FIG. 3 is an enlarged plan view showing the vicinity of a discharge port formed in the scroll compressor 11. FIG. FIG. 3 is a cross-sectional view of FIG. 2 cut along a cutting plane line III-III. It is sectional drawing which expands and shows the valve seat 91 vicinity of the section IV of FIG. 7 is a graph showing the relationship between the depth dimension δ of the escape groove 93 and the sagging length x.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 ... Scroll type compressor 25 ... Housing 33 ... Working chamber 35 ... Fixed scroll 43 ... Movable side spiral 47 ... Fixed side plate (wall part)
49 ... Fixed side spiral 79 ... Discharge port 81 ... Discharge chamber 83 ... Reed valve 89 ... Valve storage chamber 90 ... Reed valve device 92 ... Annular groove 93 ... Relief groove 94 ... Foreign material groove

Claims (6)

A compressor that compresses fluid sucked from outside and discharges the compressed fluid through a discharge port (79),
Around the opening on the downstream side of the discharge port, a valve seat (91) is formed,
A reed valve (83) that closes the discharge port by contacting the valve seat and opens the discharge port by moving away from the valve seat;
The reed valve is provided to extend from one end (86) to the other end (87),
One end of the reed valve is fixed at a predetermined fixing position,
The other end of the reed valve is provided to face the valve seat,
An annular groove (92) is formed around the valve seat,
A relief groove (93) having a depth dimension smaller than that of the annular groove is formed on one end side of the reed valve of the annular groove,
The compressor is characterized in that the escape groove is formed at least in a portion overlapping with the reed valve when viewed from the downstream side in the discharge direction (Z) of the fluid discharged from the discharge port. A housing (25);
A fixed scroll (35) fixed inside the housing and having a spiral fixed side spiral (49);
A movable scroll (43) formed between the working chamber (33) for compressing fluid and the fixed-side spiral portion, and a movable scroll (31) rotating with respect to the fixed scroll;
The compressor according to claim 1, wherein a plurality of the discharge ports are provided in communication with the working chamber. The discharge port is formed in the wall (47),
The said wall part accommodates the said reed valve, The valve accommodating chamber (89) which becomes concave shape in the opposite direction from the end surface part by the side of the discharge direction of the said wall part is formed. The compressor described in 1.   4. The groove according to claim 1, further comprising a groove (94) connected to one end side of the reed valve of the relief groove and having a depth dimension larger than that of the relief groove. 5. Compressor.   The compressor according to any one of claims 1 to 4, wherein the fluid discharged from the discharge port is carbon dioxide.   The compressor according to any one of claims 1 to 5, wherein a depth dimension of the escape groove is 0.02 mm or more and 0.7 mm or less.

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