WO2007029366A1 - Reciprocating compressor - Google Patents

Abstract

A reciprocating compressor enabling an increase in the durability of a reed valve by dispersing a stress concentrated to the base end part of the reed valve to secure its fatigue strength and further enabling an increase in the performance of the compressor. A valve plate is installed between a cylinder block in which a cylinder bore is formed and a cylinder head in which a space for temporarily storing a working fluid is formed, a port allowing the cylinder bore to communicate with the space is formed in the valve plate, and the port is opened and closed by the reed valve. The reed valve comprises a seat part (30a) formed at the tip part of a deformed area and seated at the peripheral edge of the port and a base end part (30b) fixed to the valve plate and forming the base end of the deformed area. The section modulus of the base end part (30b) is set larger than the section modulus of the seat part (30a).

Description

 Specification

 Reciprocating compressor

 Technical field

 The present invention relates to a reciprocating compressor, and in particular, a reciprocating motion in which a valve plate is arranged between a cylinder block and a cylinder head, and a port formed in the valve plate is opened and closed by a reed valve. The present invention relates to a compressor.

 Background art

 [0002] A reciprocating compressor is provided with a cylinder block formed with a cylinder bore, a piston that reciprocates linearly within the cylinder bore, and a side opposite to the side where the piston of the cylinder block is inserted. Some of them include a cylinder head in which a suction chamber and a discharge chamber for temporarily storing a working fluid are formed, and a valve plate disposed between the cylinder block and the cylinder head. In such a configuration, the cylinder bore and the suction chamber communicate with each other via a suction port provided in the valve plate, and the suction port is opened and closed by a suction valve that also has a reed valve force. .

 [0003] Such a suction valve is configured as a loose cantilever in which a deformation region is formed from a base end portion defined by a restraining edge provided on a member facing the valve plate. A seat portion seated on the periphery of the suction port is formed at the front end portion.

 [0004] Therefore, when the pressure in the cylinder bore becomes lower than the pressure in the suction chamber as the piston moves during the suction process, the deformation region of the suction valve opens the suction port blockage due to the pressure difference between the front and rear of the seat portion. The working fluid in the suction chamber is introduced into the cylinder bore through the suction port.

 [0005] A conventional suction valve is represented by a hollow portion that avoids interference with the discharge port, as represented by Figs. 2 and 3 of Patent Document 1, and Fig. 2 of Patent Document 2. As you can see, there is something without a cutout.

[0006] As shown in FIG. 10, the former suction valve gradually increases in width from the seat portion 30a seated on the periphery of the suction port 24 toward the base end portion 30b, and is closer to the center P of the cylinder bore 11. A cutout portion 44 is formed in a portion near the base end portion. This cut-out portion 44 has a discharge port. It is formed in a long hole along the axial direction of the intake valve 30 so that the port 25 faces.

The erection portions 45 formed on both sides of 4 have a total width equal to or less than the width of the seat portion 30a, and are extended so that the inner edges of both erection portions are substantially parallel to each other.

[0007] The above-mentioned base end portion 30b is a restraining edge (on the side of the base end portion 30b of the intake valve shown in FIG. 10) formed by the peripheral edge of the gasket interposed between the cylinder bore 11 and the valve plate. The constraining edge 40a provided on this gasket is defined by the broken line shown in FIG.

Formed in an arc concentric with the center P of 11!

Further, as shown in FIG. 11, the latter suction valve 30 is formed such that the width of the seat portion 30a seated on the periphery of the suction port 24 is larger than the base end portion 30b, and the seat end 30b The part 30a is formed with a substantially uniform width.

 Patent Document 1: Japanese Patent No. 3430486

 Patent Document 2: Japanese Patent No. 3608299

 Disclosure of the invention

 Problems to be solved by the invention

 [0009] By the way, the amount of deformation of the suction valve changes according to the amount of working fluid that passes through the suction port, and the greater the amount of working fluid that passes through, the greater the pressure that acts on the seat portion of the suction valve. The amount of deformation of the intake valve increases. For this reason, as described above, when the width at the base end portion is equal to or less than the width of the sheet portion, the section coefficient of the base end portion becomes relatively small, so that the base end away from the sheet portion Due to the bending moment that increases as the position is closer, the bending stress generated when the valve is opened increases near the base end, which is smaller near the seat. For this reason, allowable stress may be exceeded at the proximal end of the intake valve.

 [0010] In particular, when the restraining edge that defines the base end portion is formed in an arc shape along the valve plate side opening edge of the cylinder bore by the above-described gasket or the like, it is provided at both end portions of the base end portion of the intake valve. Stress is likely to concentrate, and there is a concern that the intake valve may be damaged during high-speed rotation and high-load operation.

[0011] In order to prevent such a situation, a recess for a stagger that restricts the maximum lift amount of the suction valve is formed in the peripheral portion where the cylinder bore of the cylinder block opens, thereby sucking a large amount of working fluid. However, a configuration is adopted in which the amount of deformation of the suction valve is kept within a predetermined value. However, from the viewpoint of reducing the passage resistance at the maximum lift, it is difficult to achieve both the compressor performance and the durability of the intake valve, which are preferable to increase the maximum lift. It was.

 [0012] From such a viewpoint, the following three methods have been considered in order to reduce the stress acting on the proximal end portion of the intake valve and increase the fatigue strength of the intake valve.

 (0 Increase the lead length of the suction valve.

 Reduce the lift amount of the GO intake valve

 (iii) Increase the radius of curvature of the arc at both ends of the base end of the intake valve

[0013] However, if the lead length of the suction valve is to be increased in order to adopt the method (0), the suction port diameter must be reduced due to the restriction of the cylinder bore diameter. If the value is reduced, the passage area of the working fluid decreases, so that the passage resistance increases tl and the performance of the compressor decreases.

 In addition, if the lift amount of the intake valve is reduced to adopt the GO method, the passage area of the working fluid is reduced, the passage resistance is increased, and the performance of the compressor is degraded.

 Furthermore, if the radius of curvature of the arc at both ends of the base end is increased in order to adopt the method (m), as a result, the deformation area of the intake valve is shortened and the spring constant of the intake valve is increased. As a result, the lift force is reduced and the passage resistance is disadvantageously increased.

 [0014] The present invention has been made in view of such circumstances, and by dispersing stress concentrated on the base end portion of the reed valve, fatigue strength is ensured and durability is increased, and compression is performed. The main issue is to provide a reciprocating compressor that can improve the performance of the compressor.

 Means for solving the problem

 [0015] As a result of earnest research on the configuration for distributing the stress at the proximal end of the reed valve, the present inventors have improved the shape of the valve body itself or improved the state of restraining the valve body. As a result, it was found that the stress generated at the base end portion can be dispersed, and the present invention has been completed.

That is, the reciprocating compressor according to the present invention has a valve plate between a cylinder block in which a cylinder bore is formed and a cylinder head in which a space for temporarily storing a working fluid is formed. A port for communicating the cylinder bore and the space is formed in the valve plate. In a configuration that is opened and closed by a force S reed valve, the reed valve is provided at a distal end portion of the deformation region and is seated on a peripheral edge of the port; and a base end of the deformation region that is fixed to the valve plate The section coefficient of the base end portion is larger than the section coefficient of the sheet portion (claim 1).

 [0017] Accordingly, since the strength of the seat portion against bending is relatively smaller than the base end portion of the reed valve, the seat portion is easily turned and the stress generated at the base end portion is dispersed in the seat portion direction. Thus, it becomes possible to reduce the maximum bending stress acting on the base end portion.

 [0018] Further, with the above-described configuration, it is effective to provide a relay portion having a smaller section modulus than that of the sheet portion in the middle of the deformation region transitioning from the sheet portion to the base end portion (contract). Claim 2). In such a configuration, the tip portion of the reed valve is more easily turned by the presence of the relay portion, and it is possible to increase the lift amount when the valve is opened and to reduce the stress generated at the base end portion. .

 [0019] In the configuration described above, the reed valve may be configured such that the width of the seat portion is smaller than the width of the base end portion and larger than the width of the relay portion (Claim 3). By adopting such a configuration, it is possible to respond by varying the width of each part of the reed valve.Therefore, it is not necessary to adopt a structure such as making the thickness of the reed valve different in each part. The adjustment of the is a nuisance.

 [0020] In particular, if the width of the reed valve is linearly reduced with the force at the base end also directed toward the relay portion, the extension lines of the outer edges on both sides intersect each other in the vicinity of the center of the port. (Claim 4) It is possible to gradually reduce the rigidity by applying force from the base end portion to the relay portion, and it is possible to make it easier to turn as the distance from the base end portion increases.

 [0021] Further, in the configuration in which the cut-out portion is formed in the portion closer to the base end portion than the relay portion of the reed valve, the erection portions formed on both sides of the cut-out portion are made wider toward the base end portion. (Claim 5). In such a configuration, the reduction of the cross-sectional coefficient due to the provision of the cut-out portion can be compensated by making the width of the erection portion wider toward the base end portion. It is possible to reduce the rigidity on the seat portion side while ensuring rigidity, and to make it easier to turn.

[0022] A reciprocating compressor according to the present invention operates with a cylinder block having a cylinder bore formed therein. A valve plate is formed between the cylinder head and a cylinder head in which a space for temporarily storing fluid is formed. A port is formed in the valve plate to communicate the cylinder bore and the space. The port is opened and closed by a lead valve. In this configuration, the reed valve is restrained by a member facing the valve plate, and has a base end portion defined by a restraining edge provided on the facing member, and the restraining edge is Alternatively, at least a part of the cylinder bore may gradually move outward from the periphery of the cylinder bore as it goes outward in the width direction (Claim 6).

[0023] In such a configuration, since the restraining edge is provided outside the peripheral edge of the cylinder bore, even if the reed valve has a shape that spreads the force on the side of the seat portion, the base end portion force has a sufficiently long deformation region. In addition, the stress is not concentrated on both end portions of the base end portion, and the stress can be dispersed.

[0024] As an example, when the constraint edge is formed of an arc, the radius of curvature of the constraint edge that is not concentric with the center of the cylinder bore is preferably larger than the radius of the cylinder bore. . If the center of curvature of the constraining edge is concentric with the center of the cylinder bore, the state of stress concentration on both sides of the base end cannot be changed, and the above disadvantage cannot be overcome. By doing so, it is possible to ensure a long deformation region length of the reed valve and to disperse the stress at the base end to the center side by appropriately selecting the position of the center of curvature and the radius of curvature. Stress concentration on a specific part can be avoided.

 [0025] The center of curvature of the restraining edge is preferably provided on the axis of the reed valve (claim 8). In such a configuration, even when the axis of the reed valve does not pass through the center of the cylinder bore, it is possible to make the stress distribution at the base end symmetrical with respect to the axis, and the imbalance of stress acting during deformation Can be prevented.

 [0026] The member facing the valve plate constituting the restraining edge may be a gasket interposed between the cylinder block and the cylinder head (Claim 9) or a cylinder block. Brief Description of Drawings

FIG. 1 is a cross-sectional view showing a configuration example of a reciprocating compressor.

FIG. 2 is an exploded perspective view showing various parts interposed between the cylinder block and the cylinder head. FIG. 3 is a plan view showing a suction valve seat.

 FIG. 4 is an enlarged view showing a suction valve formed on the suction valve seat of FIG.

 FIG. 5 is an enlarged view showing a through hole portion of a gasket corresponding to the suction valve of FIG.

 FIG. 6 is a plan view showing another configuration example of the intake valve seat.

 FIG. 7 is an enlarged view showing a suction valve formed on the suction valve seat of FIG.

 FIG. 8 is an enlarged view showing a through hole portion of a gasket corresponding to the suction valve of FIG.

 [Fig. 9] Fig. 9 is a plan view showing a layout of various parts interposed between the cylinder block and the cylinder head.

 FIG. 10 is a view showing a conventional suction valve.

 FIG. 11 is a view showing another configuration of a conventional suction valve.

 Explanation of symbols

[0028] 1 cylinder block

 2 Valve plate

 3 Cylinder head

 11 Cylinder bore

 22 Suction chamber

 24 Suction port

 30 Suction valve

 30a Seat part

 30b Base end

 30c Relay section

 33 Gasket

 40a Restraint edge

 44 Cutout

 BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 shows a reciprocating compressor according to an embodiment of the present invention. This reciprocating compressor has a cylinder block 1 and a valve plate 2 on the rear side of the cylinder block 1. The cylinder head 3 and the front housing 5 are formed so as to cover the cylinder block 1 and define the crank chamber 4 on the front side of the cylinder block 1. The housing 5, the cylinder block 1, the valve plate 2, and the cylinder head 3 are fastened in the axial direction by fastening bolts 6.

A crank chamber 4 provided by the front housing 5 and the cylinder block 1 accommodates a drive shaft 7 projecting from one end force S front nose and the wing 5.

 One end of the drive shaft 7 is rotatably supported by the front housing 5 via the radial bearing 8, and the other end of the drive shaft 7 rotates to the cylinder block 1 via the radial bearing 9 and the thrust bearing 10. Supported as possible.

[0031] The cylinder block 1 is formed with a plurality of cylinder bores 11 at predetermined intervals in the circumferential direction around the drive shaft 7, and a piston 12 is slidably inserted into each cylinder bore 11. Yes.

 A thrust flange 15 that rotates integrally with the drive shaft 7 is fixed to the drive shaft 7 in the crank chamber 4. The thrust flange 15 is rotatably supported on an inner wall surface of the front housing 5 formed substantially perpendicular to the drive shaft 7 via a thrust bearing 16. A swash plate 18 is connected to the thrust flange 15 via a link member 17.

 [0033] The swash plate 18 is tiltably held via a hinge ball 19 provided on the drive shaft 7! As a result, it will rotate integrally with the rotation of the thrust flange 15! /. Then, the engaging portion 12a of the piston 12 is moored at the peripheral portion of the swash plate 18 through a pair of shears 20 provided at the front and rear.

 Therefore, when the drive shaft 7 rotates, the swash plate 18 rotates with this, and the rotational motion of this swash plate 18 is converted into the reciprocating linear motion of the piston 12 via the shear 20, and the inside of the cylinder bore 11. At this point, the volume of the compression chamber 21 defined between the piston 12 and the valve plate 2 is changed.

The cylinder head 3 includes a suction chamber 22 and a discharge chamber 23 formed around the suction chamber 22. The valve plate 2 has a suction chamber 22 and a compression chamber via a suction valve 30. 21 Discharge chamber 23 and compression chamber 21 (cylinder bore 1 via a suction port 24 communicating with (cylinder bore 11) and a discharge valve 31 Discharge ports 25 communicating with 1) are formed at predetermined intervals in the circumferential direction.

As shown in FIG. 2, a suction valve seat 32 is overlapped with the end face of the valve plate 2 on the cylinder block 1 side, and the cylinder block 1 is overlapped with the suction valve seat 32 via a gasket 33. Has been. A discharge valve sheet 34 formed with a discharge valve 31 is superimposed on the cylinder head side end surface of the valve plate 2, and the cylinder head 3 is superimposed on the discharge valve sheet 34 via a gasket 35. ing. The cylinder block 1, the gasket 33, the suction valve sheet 32, the valve plate 2, the discharge valve seat 34, and the gasket 35 are positioned by a positioning pin 36 and pressed by a bolt 37 screwed into the cylinder block 1. It is fixed in the state.

 As shown in FIG. 3, the suction valve seat 32 is composed of an assembly of a plurality of suction valves 30 that open and close the suction port 24. The suction valve 30 includes a cylinder bore 11 The holes 32a and 32b for inserting the bolts 6 and 37, the holes 32c for passing the positioning pins and the like are formed.

 [0038] As shown in FIG. 4, each intake valve 30 is configured by a part of the intake valve seat 32, and is provided so as to surround the periphery and connects adjacent intake valves to each other. Yes It is formed integrally with the connecting part 38. The suction valve 30 is configured as a reed valve made of a cantilever beam having a uniform thickness, and a seat portion 30a seated on the periphery of the suction port 24 is formed at the tip of the deformation region. The seat portion 30a is formed in a shape substantially similar to the shape of the suction port 24. When the suction port 24 has a circular cross section, the seat portion 30a is formed in a circular shape.

 [0039] Further, in the middle of the transition from the sheet portion 30a to the base end portion 30b serving as the base end of the deformation region, a relay portion 30c formed with a width L2 smaller than the width of the sheet portion 30a is formed. The width gradually increases from the portion 30c to the base end portion 30b.

 [0040] The width L1 of the seat portion 30a is formed to be smaller than the width L3 of the base end portion 30b, and the width of the suction valve 30 is linear in the portion where the force of the base end portion 30b also moves toward the relay portion 30c. The extension lines of the outer edges on both sides of this part intersect each other in the vicinity of the center S of the suction port 24 (in this example, intersect at the center S of the suction port 24).

Therefore, in the intake valve 30, the section coefficient of the base end part 30b is larger than the section coefficient of the seat part. In addition, the section modulus of the relay portion 30c is smaller than the section modulus of the sheet portion 30a.

 [0042] In the gasket 33, through holes 40 communicating with the cylinder bores 11 are formed at equal intervals in the circumferential direction according to the number of the cylinder bores 11, and holes 42a and 42b for positioning the bolts 6 and 37 and positioning are provided. A hole 42c or the like (shown in FIG. 2) for inserting the pin 36 is formed.

 The restraint state of the suction valve 30 is determined by the shape of the through hole 40 of the gasket 33. As shown in FIG. 5, the suction valve 30 is formed by the peripheral edge of the through hole 40 formed in the gasket 33. A restraining edge 40a is formed to form a boundary for restraining the air, and the proximal end portion 30b of the intake valve 30 is defined by the restraining edge 40a!

 [0044] The constraining edge 40a provided on the gasket 33 is formed so as to gradually move away from the periphery of the cylinder bore 11 toward the outer side in the width direction. In this example, the constraining edge 40a is formed in an arc shape and constrained. The center of curvature Q of the edge 40a is not concentric with the center P of the cylinder bore 11. The radius of curvature of the restraining edge 40a is set on the axis of the intake valve 30 so as to be larger than the radius of the cylinder bore 11. In this example, the axis M of the suction valve 30 does not pass through the center P of the cylinder bore 11 and is formed at a biased position, and a discharge port 25 is formed on the side opposite to the biased side. And

 Reference numeral 50 denotes a pressure control valve that adjusts the crank chamber pressure to adjust the piston stroke, that is, the discharge capacity.

 [0045] Therefore, in the above-described configuration, since the section modulus of the base end portion 30b of the suction valve 30 is formed larger than the section modulus of the seat portion 30a, the strength of the seat portion 30a against bending is increased. It is relatively smaller than the above, and it is easy to turn in the sheet portion 30a, and the maximum bending stress acting on the base end portion 30b can be reduced by dispersing the stress generated in the base end portion 30b. .

 Accordingly, the lift amount of the suction valve 30 can be increased and the stress acting on the base end portion 30b can be reduced, so that the performance of the compressor can be improved, and the base end of the suction valve 30 can be increased. The stress acting on the portion 30b can be dispersed to ensure fatigue strength, and the durability of the intake valve 30 can be enhanced.

[0047] In the above configuration, in the above configuration, during the transition from the seat portion 30a to the base end portion 30b, Since the relay part 30c having a smaller section modulus than the seat part 30a is provided, the presence of the relay part 30c makes it easier for the tip part of the intake valve 30 to bend, and the lift amount when the valve is opened can be increased. Thus, the stress at the base end portion 30b can be reduced.

[0048] In particular, when the section modulus is adjusted by forming each part with a uniform thickness and adjusting the width as in the above-described configuration, the adjustment of the stress distribution at each part is impeded. It becomes.

 [0049] Further, the width of the suction valve 30 is linearly reduced from the base end portion 30b to the relay portion 30c, and the extension lines of the outer edges on both sides intersect with each other in the vicinity of the center S of the suction port 24. Therefore, it is possible to gradually reduce the rigidity by directing the force from the base end portion 30b to the relay portion 30c, and it is possible to make it easier to turn away from the base end portion 30b.

 [0050] Further, in the above-described configuration, the center of curvature Q of the restraining edge 40a is also shifted from the center P force of the cylinder bore 11, and the restraining edge provided on the gasket 33 is formed by forming the curvature radius of the restraining edge 40a larger than the radius of the cylinder bore 11. 40a is configured to gradually move away from the periphery (valve plate side opening edge) of the cylinder bore 11 as the force is directed outward in the width direction, so even if the intake valve 30 is formed in a shape that widens from the seat portion 30a, the lead The length can be secured, and the stress can be dispersed without concentrating on both sides of the base end portion 30b. Therefore, the fatigue strength at the proximal end 30b of the intake valve 30 can be secured to increase the durability of the intake valve 30, and the tip end portion of the intake valve can be easily squeezed. Therefore, it is possible to achieve both the performance of the compressor and the durability of the intake valve.

 [0051] Since the center of curvature Q of the restraining edge 40a is provided on the axis of the intake valve 30, the axis M of the intake valve 30 does not pass through the center P of the cylinder bore 11 as in the above configuration example. However, the stress distribution at the base end 30b can be made symmetrical with respect to the axis M, and the imbalance of the stress acting during deformation can be prevented.

FIG. 6 and FIG. 7 show another configuration example of the intake valve 30 of the compressor according to the present invention. In this example, the suction valve 30 formed on the suction valve seat 32 is formed such that its axis M passes through the center P of the cylinder bore 11. For this reason, the suction valve 30 is formed with a cut-out portion 44 in a portion closer to the base end portion 30b than the relay portion 30c, and a discharge port 25 is formed in the valve plate 2 so as to face the cut-out portion 44. Drying of valve 30 and discharge port 25 I try to prevent interference.

 [0053] On both sides of the cut-out portion 44, an erection portion 45 that extends from the base end portion 30b to the relay portion 30c is formed, and the erection portion 45 is formed wider toward the base end portion 30b in accordance with the direction force. In particular, in this example, the extension line of the inner edge of the erection part 45 intersects in the vicinity of the center S of the suction port 24 (in this example, intersects with the center S of the suction port 24).

 [0054] Similarly to the configuration example, the suction valve 30 is a relay formed smaller than the width of the seat portion 30a during the transition from the seat portion 30a to the proximal end portion 30b serving as the proximal end of the deformation region. A portion 30c is formed, and the width is gradually increased from the relay portion 30c to the base end portion 30b. The width of the seat portion 30a is smaller than the sum of the widths L4 of the base end portions 45a of the respective erection portions 45, and suction is performed at a portion where the seat portion 30a moves from the base end portion 30b to the relay portion 30c. The width of valve 30 decreases linearly, and the extension of the outer edge on both sides of this part is the center of the port.

 It intersects near S (in this example, it intersects at the center S of the suction port 24).

Therefore, the suction valve 30 is formed such that the section coefficient of the base end part 30b is larger than the section coefficient of the seat part 30a, and the relay part provided in the middle of the transition from the seat part 30a to the base end part 30b. The section modulus of 30c is formed smaller than the section modulus of the sheet part 30a.

[0056] Further, in this example, the restraining edge 40a provided on the gasket 33 is gradually separated from the periphery of the cylinder bore 11 toward the outside as it goes outward in the width direction, as shown in FIG. The center of curvature Q of the restraining edge 40a is provided on the axis M of the intake valve 30 passing through the center P of the cylinder bore 11 in that it is formed in an arc shape. Since other configurations are the same as those in the above configuration example, the same numbers are assigned to the same portions, and descriptions thereof are omitted.

 [0057] In such a configuration, the same operational effects as in the above configuration example can be obtained, and even when the cutout portion 44 is formed in the intake valve 30, the base end portion side that can be easily turned on the seat portion side is provided. It is possible to disperse the stress, and it is possible to improve both the performance of the compressor and the durability of the suction valve.

[0058] In each of the above configuration examples, the center of the seat portion 30a of the suction valve 30 (the center S of the suction port 24) is the center of the drive shaft 7 and the center of the discharge port 25 as shown in FIG. Connect center C It is preferable that they are arranged on a line (the drawing shows an example in which the suction chamber is formed around the discharge chamber). By adopting such a configuration, the partition wall 51 that partitions the suction chamber 22 and the discharge chamber 23 formed in the cylinder head 3 can be formed into a cylindrical shape, which contributes to an improvement in the efficiency of the compressor. (In FIG. 9, E is a bead formed by raising a part of the gasket 33, and surrounds the periphery of the cylinder bore 11 in a ring shape along the edge of the through hole 40).

 In the above-described embodiment of the present invention, the use of the compressor is not particularly mentioned, but it is particularly effective in the C02 compressor having a small cylinder bore diameter. Further, in the above-described configuration, the force edge shown in the example in which the member constituting the restraining edge 40a is the gasket 33 interposed between the cylinder block 1 and the valve plate 2 does not constitute the restraining edge. Also, you can make a restraint edge on the cylinder block 1!

 Further, in the above-described configuration, a configuration similar to the force shown in the configuration example applied to the suction valve may be applied to the discharge valve.

Claims

The scope of the claims  [1] A valve plate is provided between a cylinder block in which a cylinder bore is formed and a cylinder head in which a space for temporarily storing a working fluid is formed, and the cylinder bore and the space communicate with the valve plate. In a reciprocating compressor in which a port is formed and this port is opened and closed by a reed valve,  The reed valve has a seat portion provided at a distal end portion of the deformation region and seated on a peripheral edge of the port, and a sectional modulus of a proximal end portion serving as a proximal end of the deformation region is defined as a sectional modulus of the seat portion. A reciprocating compressor characterized in that it is larger.  [2] The reciprocating compressor according to [1], wherein a relay section having a smaller section modulus than that of the sheet section is provided in the middle of the deformation region that moves from the sheet section to the base end section. 3. The reciprocating compressor according to claim 2, wherein the reed valve has a width of the seat portion smaller than a width of the base end portion and larger than a width of the relay portion. [4] The width of the reed valve linearly decreases from the base end portion toward the relay portion, and extension lines of outer edges on both sides intersect each other in the vicinity of the center of the port. Item 4. The reciprocating compressor according to item 3. [5] In the reed valve, a hollow portion is formed in a portion closer to the base end portion than the relay portion, and the erection portions formed on both sides of the hollow portion become wider toward the base end portion. 2. The reciprocating compressor according to claim 1, wherein the compressor is a reciprocating compressor. [6] A valve plate is provided between the cylinder block in which the cylinder bore is formed and the cylinder head in which a space for temporarily storing the working fluid is formed, and the cylinder bore and the space communicate with the valve plate. In a reciprocating compressor in which a port is formed and this port is opened and closed by a reed valve,  The reed valve is constrained by a member facing the valve plate, and has a base end portion defined by a restraining edge provided on the facing member, and at least a part of the restraining edge has a width. A reciprocating compressor characterized in that the cylinder bore is gradually separated outward from the periphery of the cylinder bore as it goes outward in the direction. [7] The constraint edge is formed in an arc shape, and the center of curvature thereof is not concentric with the center of the cylinder bore. The curvature radius of the constraint edge is larger than the radius of the cylinder bore! / ヽ. The reciprocating compressor according to claim 6. 8. The reciprocating compressor according to claim 7, wherein the center of curvature of the restraining edge is provided on an axis of the reed valve. 9. The reciprocating compressor according to claim 6, wherein the member facing the valve plate is a gasket interposed between the cylinder block and the cylinder head.