WO2016052318A1

WO2016052318A1 - Reciprocating compressor

Info

Publication number: WO2016052318A1
Application number: PCT/JP2015/077036
Authority: WO
Inventors: 宏金井; ツィリアックミヒャル; 直樹神宮
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2014-09-30
Filing date: 2015-09-25
Publication date: 2016-04-07
Also published as: JP2016070167A

Abstract

[Problem] To provide a reciprocating compressor which is configured so that the entire region, in the width direction, of the base end of a discharge valve can be easily held down, thereby enabling stable valve opening operation without the twisting of the discharge valve, and which is also configured so that the width of a discharge chamber is not reduced, thereby preventing an increase in the loss of pressure of discharge gas. [Solution] A compressor is provided with: a cylinder head 3 having a suction chamber 31 formed in the radial center thereof and having a discharge chamber 32 formed annularly around the suction chamber 31; and reed valve type discharge valves 71 provided on the cylinder head 3 side of a valve plate 2 and opening and closing discharge holes 27 formed in the valve plate 2. The front end of each of the discharge valves 71 is disposed radially outside the base end thereof so as to be circumferentially offset from the base end, and the base end of the discharge valve 71 is pressed upon and affixed to the valve plate 2 by a partition wall 36 for separating the discharge chamber 32 and the suction chamber 31.

Description

Reciprocating compressor

The present invention relates to a reciprocating compressor, and in particular, a suction chamber is formed at the center of the cylinder head in the radial direction, and an annular discharge chamber is formed outside the suction chamber of the cylinder head, corresponding to a plurality of cylinder bores. The present invention relates to a compressor in which a plurality of discharge valves are arranged in the circumferential direction.

In a conventional reciprocating compressor, a piston is accommodated in a cylinder bore of a cylinder block so as to reciprocate, and a cylinder head is fixed to a rear portion of the cylinder block by a fastening bolt via a valve plate.

The cylinder head is partitioned into a suction chamber and a discharge chamber. The cylinder bore and the suction chamber communicate with each other through a suction hole formed in a valve plate that is opened and closed by a suction valve. Is communicated via a discharge hole formed in a valve plate that is opened and closed by a discharge valve. When the pressure in the cylinder bore decreases during the piston suction process, the suction valve elastically deforms due to the pressure difference before and after the suction valve. When the working gas flows into the cylinder bore from the suction chamber and into the cylinder bore, and the pressure in the cylinder bore rises during the piston discharge process, the suction valve comes into contact with the seat surface around the suction hole, Due to the pressure difference before and after the discharge valve, the discharge valve is elastically deformed and separated from the seat surface around the discharge hole, and the compressed gas in the cylinder bore flows into the discharge chamber. That.

In such a compressor, when the suction chamber is formed in the center of the cylinder head and the discharge chamber is formed in an annular shape on the outer periphery of the cylinder head (around the suction chamber), the suction chamber is formed on the valve plate. The discharge valve 71 that opens and closes the discharge hole is provided in the width direction (radial direction) of the annular discharge chamber 32 as shown in FIG. 9A, for example. As shown in FIG. 9B, the base end portion 71b is often pressed and fixed to the valve plate by the end face of the partition wall 36 that partitions the suction chamber 31 and the discharge chamber 32 (for example, Patent Documents). 1).

However, when the discharge valve 71 is disposed in the width direction (radial direction) of the annular discharge chamber 32, the refrigerant gas discharged into the discharge chamber 32 by pushing the discharge valve 71 from the cylinder bore is discharged. It collides with the inner surface of the outer peripheral wall 35 of the chamber 32, and then the direction of the flow of the refrigerant gas is converted into the circumferential direction. In addition, since the refrigerant gas flow is divided in a direction opposite to the circumferential direction of the cylinder head 3, it collides with the refrigerant gas flow discharged from the adjacent cylinder bore, resulting in pressure loss and compressor efficiency. It was one of the factors that lowered

On the other hand, as shown in FIG. 10A, a compressor is proposed in which a plurality of discharge valves 71 are arranged on a disc-shaped discharge valve seat 70 on the outer periphery of the valve plate in the circumferential direction of the cylinder head. (See Patent Document 2).
In such a configuration, the refrigerant gas discharged into the discharge chamber 32 does not directly collide with the inner surface of the outer peripheral wall 35 that defines the discharge chamber 32, and flows smoothly along the inner surface of the outer peripheral wall 35 as it is. (Refer to FIG. 10B). Therefore, in such a configuration, there is an advantage that pressure loss hardly occurs and the compression efficiency of the compressor can be improved.

JP 2007-64196 A JP 2005-320902 A

However, in the configuration in which the discharge valve extends in the circumferential direction of the cylinder head, the discharge valve seat cannot be stably held only by the partition wall that partitions the discharge chamber and the suction chamber. ), The outer shape of the discharge valve seat 70 must be formed large so that the outer peripheral edge of the discharge valve seat 70 is also sandwiched between the cylinder head 3 and the valve plate. For this reason, the outer shape of the discharge valve seat 70 becomes large, and the component cost increases.

Further, in the configuration in which the discharge valve 71 extends in the circumferential direction of the cylinder block, the base end portion of the discharge valve 71 cannot be pressed by the partition wall 36 that partitions the suction chamber 31 and the discharge chamber 32. The base end portion of the discharge valve 71 is pressed by a bolt screw seat surface 38 that is formed to bulge inward from the outer peripheral wall 35 of the head 3. Therefore, it is impossible to hold down the entire width direction of the base end portion of the discharge valve 71, and there is a concern that the discharge valve 71 may be damaged due to a slight twist in the movement of the discharge valve 71 when the valve is opened.

Further, in the structure in which the gasket 80 is interposed between the discharge valve seat 70 and the cylinder head 3 and the discharge valve seat 70 and the gasket 80 are sandwiched between the valve plate 2 and the outer peripheral wall 35 of the cylinder head 3. As shown in FIG. 10C, the stepped portion 81a is formed on the annular peripheral edge 81 of the gasket 80 and the outer peripheral wall 35 of the cylinder head 3 so that the outer peripheral edge of the discharge valve seat 70 is not exposed to the outside of the compressor. 35a is formed, and the outer peripheral edge of the discharge valve seat 70 is sandwiched between the step portion and the valve plate 2. For this reason, it is necessary for the outer peripheral wall 35 of the cylinder head 3 to secure the width of both the flat portion for sandwiching the gasket 80 and the stepped portion 35a for sandwiching the outer peripheral edge of the discharge valve seat 70. The wall thickness of the outer peripheral wall 35 is increased, and accordingly, the outer diameter and weight of the cylinder head 3 (and hence the compressor) are increased.

The present invention has been made in view of such circumstances, and it is possible to prevent twisting of the discharge valve by facilitating pressing of the entire width direction of the base end portion of the discharge valve while ensuring a smooth flow of the refrigerant gas. The main problem is that stable valve opening operation can be achieved by avoiding the problem, and further, the disadvantages of increasing the discharge valve seat and increasing the thickness of the outer peripheral wall of the cylinder head are avoided, thereby reducing the component cost. It is said. Further, even when a gasket is interposed between the discharge valve seat and the cylinder head, it is an object to avoid an increase in the outer shape and weight of the cylinder head.

In order to achieve the above object, a reciprocating compressor according to the present invention includes a cylinder block in which a plurality of cylinder bores for reciprocally accommodating a piston are arranged around a shaft, and an end of the cylinder block. A valve plate formed with a suction hole and a discharge hole corresponding to each cylinder bore, a suction chamber that is assembled to the cylinder block with the valve plate interposed therebetween, and communicates with each suction hole; A cylinder head having a discharge chamber communicating with each of the discharge holes, the suction chamber being formed in a central portion in a radial direction, and the discharge chamber being formed in an annular shape around the suction chamber; A reed valve type intake valve provided on the cylinder block side of the plate for opening and closing the intake hole; and the cylinder of the valve plate And a reed valve type discharge valve that opens and closes the discharge hole. The reciprocating motion of the piston sucks the refrigerant gas in the suction chamber into the cylinder bore through the suction hole and compresses it. In the configuration in which the refrigerant gas discharged is discharged into the discharge chamber through the discharge hole, the discharge valve is disposed radially outside the base end portion and shifted in the circumferential direction. The base end portion of the discharge valve is pressed and fixed to the valve plate by a partition wall that partitions the discharge chamber and the suction chamber.

Therefore, according to the configuration of the present invention, the discharge valve has its distal end portion disposed radially outside the base end portion and is displaced in the circumferential direction. Thus, the refrigerant gas can be guided in the circumferential direction of the annular discharge chamber of the cylinder head, and a smooth gas flow can be ensured. Further, since the base end portion is disposed radially inward from the tip end portion, the entire width direction region of the base end portion of the discharge valve is easily pressed and fixed to the valve plate by the partition wall that partitions the discharge chamber and the suction chamber. .

As a result, in order to press the base end portion of the discharge valve, it is necessary to increase the bolt screw seat surface bulging inward from the outer peripheral wall of the cylinder head, or to increase the member forming the discharge valve. There is no need to clamp the cylinder head on the outer peripheral wall, and the component cost can be reduced.

Here, the width of the discharge valve may be gradually reduced from the distal end portion to the proximal end portion. According to such a configuration, the required width of the base end portion pressed by the cylinder head can be shortened, the entire width direction of the base end portion can be more reliably pressed by the partition wall, and the discharge chamber A large width (width of the discharge gas passage) can be secured.

When the discharge holes are arranged on a pitch circle centered on the shaft, the axis of the discharge valve (the phantom line passing through the center of the base end and the center of the tip of the discharge valve) is the pitch circle. It is preferable to incline in the range of 30 to 60 degrees with respect to the tangent at the portion where the discharge hole is provided.

In addition, when a gasket is interposed between the discharge valve and the valve plate, a retainer that confronts the discharge valve and regulates the lift amount of the discharge valve is integrally formed on the gasket. The gasket is connected to both sides of the portion where the distal end portion of the discharge valve is opposed to the portion where the proximal end portion of the discharge valve is opposed to the gasket, and the portion of the gasket adjacent to the both side portions of the retainer is The valve plate is pressed and fixed to the valve plate by an end surface of the partition wall and a bolt screw seat surface formed inwardly from the outer peripheral wall of the cylinder head, and a base end portion of the retainer and a base end portion of the discharge valve are You may make it overlap and press-fix to the said valve plate with the said partition.

According to such a configuration, the portion of the gasket adjacent to both sides of the retainer is pressed and fixed to the valve plate by the end surface of the partition wall and the bolt screw seat surface formed inward from the outer peripheral wall of the cylinder head. (The gasket part adjacent to the inner side of the retainer is pressed and fixed to the valve plate by the end face of the partition wall, and the gasket part adjacent to the outer side of the retainer is fixed to the valve plate by the bolt threaded seating surface. It is unnecessary to use the outer peripheral wall of the cylinder head to sandwich the gasket portion adjacent to the side of the retainer. Therefore, the thickness of the outer peripheral wall of the cylinder head can be reduced, and the cylinder head can be reduced in size and weight.

In addition, when the discharge valves corresponding to the plurality of cylinder bores are formed integrally with the discharge valve forming plate, the peripheral edge of the connecting portion that connects the discharge valves of the discharge valve forming plate is also formed by the partition wall. It is good to press and fix to the plate.
According to such a configuration, not only the base end portion of the discharge valve, but also the peripheral edge of the portion connecting the discharge valves is pressed and fixed to the valve plate by the partition wall, so that the fixed state of the discharge valve can be further strengthened. In addition, it is possible to ensure a more stable opening / closing operation of the discharge valve.

As described above, according to the present invention, in the reciprocating compressor having the cylinder head in which the suction chamber is formed in the center in the radial direction and the annular discharge chamber is formed outside thereof, the tip of the discharge valve Since the part is arranged radially outside the base end part and shifted in the circumferential direction, the refrigerant gas discharged from the discharge valve is moved in the circumferential direction of the annular discharge chamber formed in the cylinder head. Therefore, a smooth gas flow can be ensured.

Even when the base end of the discharge valve is pressed and fixed to the valve plate by a partition wall that separates the discharge chamber and the suction chamber, the tip of the discharge valve is inclined outward with respect to the circumferential direction of the cylinder head, Since the base end portion of the valve can be disposed closer to the center of the cylinder head, the entire width direction region of the base end portion of the discharge valve can be easily pressed and fixed to the valve plate by the partition wall.

As a result, the entire partition in the width direction of the base end portion of the discharge valve can be pressed and fixed by the partition wall that partitions the discharge chamber and the suction chamber, so that there is no inconvenience that twisting occurs when the discharge valve is opened. It is possible to eliminate the risk of damage.

Further, since the base end portion of the discharge valve is pressed and fixed to the valve plate by a partition wall that partitions the discharge chamber and the suction chamber, in order to press the base end portion of the discharge valve, it expands inward from the outer peripheral wall of the cylinder head. It is no longer necessary to increase the formed bolt threaded seating surface, the width of the discharge chamber (the width of the discharge gas passage) can be secured, and the risk of an increase in pressure loss can be avoided.
In addition, since it is not necessary to form a large member (discharge valve seat) for forming the discharge valve and hold it between the outer peripheral walls of the cylinder head, it is possible to reduce the component cost.

In addition, by gradually reducing the width of the discharge valve from the distal end portion to the proximal end portion, it becomes possible to reduce the necessary area to be pressed at the proximal end portion of the discharge valve, and the width of the discharge chamber can be reduced as much as the pressure allowance can be reduced. It is possible to ensure a larger (width of the discharge gas passage).

In addition, when a gasket is interposed between the discharge valve and the valve plate, the gasket portion adjacent to both sides of the retainer formed integrally with the gasket is placed inside from the end face of the partition wall and the outer peripheral wall of the cylinder head. By clamping and fixing between the valve plate and the bolt screw seating surface formed on the bulge, and by pressing and fixing the base end of the retainer and the base end of the discharge valve to the valve plate by a partition wall, Since it is not necessary to hold the member (discharge valve seat) forming the discharge valve between the outer peripheral wall of the cylinder head and the valve plate, the thickness of the outer peripheral wall of the cylinder head can be reduced. It is possible to avoid an increase in weight, and hence an increase in the external shape and weight of the compressor, and to reduce the size and weight of the cylinder head 3 (and pulling it as a compressor). It is possible.

Fig.1 (a) is sectional drawing which shows the compressor based on this invention, FIG.1 (b) is the end elevation which looked at the cylinder block from the axial direction. FIG. 2 is an exploded perspective view of components assembled on the cylinder head side with respect to the cylinder block. FIG. 3 is an enlarged sectional view showing the assembled state of the component parts before and after the valve plate. FIG. 4 is a view of a part of the valve plate as viewed along the axial direction from the front side. FIG. 5 is a view of a part of the cylinder head as viewed along the axial direction from the front side. FIG. 6 is a view of a part of the discharge valve seat as viewed along the axial direction from the front side. FIG. 7 is a view of a part of the gasket interposed between the discharge valve seat and the cylinder head as viewed in the axial direction from the front side. FIG. 8A is a view in which the gasket shown in FIG. 7 is overlapped on the cylinder head shown in FIG. 5 as viewed from the front side along the axial direction, and FIG. 8B is a view shown in FIG. FIG. 7 is a view of the state in which the discharge valve seats shown in FIG. FIG. 9 is a view showing an example of a conventional discharge valve, (a) is a view showing a discharge valve seat, (b) is an end view of the cylinder head as viewed from the front side, and (c) is a view showing the discharge valve. It is a figure explaining the flow of the working fluid discharged via. FIG. 10 is a view showing another example of a conventional discharge valve, where (a) is a view showing a discharge valve seat, (b) is an end view of the cylinder head viewed from the front side, and (c) is a discharge view. It is a figure which shows the state which assembled | attached the valve to the cylinder head.

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1A shows a reciprocating compressor according to the present invention. The reciprocating compressor is assembled so as to cover a cylinder block 1, a cylinder head 3 assembled to the rear side of the cylinder block 1 via a valve plate 2, and a front side of the cylinder block 1. A front housing 5 defining a crank chamber 4 on the front side of the block 1 is provided. The front 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 to form a housing.

A crank chamber 4 defined by the front housing 5 and the cylinder block 1 accommodates a shaft 7 whose front end protrudes from the front housing 5. A drive pulley (not shown) is provided at a portion of the shaft 7 protruding from the front housing 5 so that rotational power applied to the drive pulley is transmitted to the shaft 7 via the clutch plate.

Further, the front end side of the shaft 7 is hermetically sealed with the front housing 5 via a seal member 10 provided between the front housing 5 and is rotatably supported by a radial bearing 11. The rear end side of the shaft 7 is rotatably supported via a radial bearing 13 that is accommodated in an accommodation hole 12 formed in the approximate center of the cylinder block 1. Here, the

radial bearings

11 and 13 may be rolling bearings or plain bearings.

As shown in FIG. 1 (b), the cylinder block 1 is arranged at equal intervals on the accommodation hole 12 in which the radial bearing 13 and the like are accommodated, and on the circumference centering on the accommodation hole 12. A plurality of cylinder bores 14 are formed, and a single-headed piston 15 is inserted into each cylinder bore 14 so as to be reciprocally slidable.

A thrust flange 16 that rotates integrally with the shaft 7 is fixed to the shaft 7 in the crank chamber 4. The thrust flange 16 is rotatably supported on an inner wall surface of the front housing 5 formed substantially perpendicular to the shaft 7 via a thrust bearing 17. A swash plate 21 is connected to the thrust flange 16 via a link member 20.

The swash plate 21 is held so as to be tiltable via a hinge ball 22 provided on the shaft 7, and rotates integrally with the rotation of the thrust flange 16. And the engaging part 15a of the piston 15 is moored by the peripheral part of the swash plate 21 via the pair of shoes 23 provided in the front and back.

Therefore, when the shaft 7 is rotated, the swash plate 21 is rotated accordingly, and the rotational motion of the swash plate 21 is converted into the reciprocating linear motion of the piston 15 via the shoe 23, and the piston 15 and the valve are disposed in the cylinder bore 14. The volume of the compression chamber 25 defined between the plate 2 and the plate 2 is changed.

The valve plate 2 is formed with a suction hole 26 and a discharge hole 27, which will be described later, corresponding to each cylinder bore 14, and the cylinder head 3 has a suction chamber 31 for storing the working fluid supplied to the compression chamber 25. And a discharge chamber 32 for storing the working fluid discharged from the compression chamber 25 is provided. In this example, the suction chamber 31 is formed in the central portion in the radial direction of the cylinder head 3, and the discharge chamber 32 is formed in an annular shape around the suction chamber 31.
The suction chamber 31 can communicate with the compression chamber 25 through the suction hole 26 opened and closed by a later-described suction valve 51, and the discharge chamber 32 is opened and closed by a later-described discharge valve 71. It is possible to communicate with the compression chamber 25 via

In the present configuration example, the air supply passage 40 that connects the discharge chamber 32 and the crank chamber 2 is formed by the

passages

40a, 40b, and 40c formed in the cylinder head 3, the valve plate 2, and the cylinder block 1. The cylinder head 3 is provided with a pressure control valve 41 for adjusting the opening degree of the air supply passage 40. Further, an extraction passage 43 for allowing the working fluid flowing into the crank chamber 4 to escape to the suction chamber 31 includes a communication passage 44 formed in the shaft 7, an orifice hole 45 provided in the valve plate 2 communicating therewith, and the like. It is formed by.
Therefore, by adjusting the valve opening degree of the pressure control valve 41 provided in the middle of the air supply passage 40, the amount of working fluid supplied from the discharge chamber 32 to the crank chamber 4 is adjusted, and the pressure in the crank chamber is reduced. It is controlled and the piston stroke, that is, the discharge amount is adjusted.

Incidentally, between the valve plate 2 and the cylinder block 1, as shown in FIG. 2, a suction valve seat 50 that is attached to be overlapped on the cylinder block side end surface of the valve plate 2, and the suction valve seat 50. A gasket 60 is provided which is overlapped and fixed between the valve plate 2 and the cylinder block 1.
In addition, a discharge valve seat 70 that is mounted on the cylinder head side end surface of the valve plate 2 is mounted between the valve plate 2 and the cylinder head, and the valve plate 2 and the cylinder are stacked on the discharge valve seat 70. A gasket 80 that is sandwiched and fixed between the head 3 and the head 3 is provided.
The cylinder block 1, the gasket 60, the suction valve seat 50, the valve plate 2, the discharge valve seat 70, the gasket 80, and the cylinder head 3 are positioned by a positioning pin (not shown), inserted from the front housing side, and screwed into the cylinder head. As shown in FIG. 3, the fastening bolts 6 are fixed in a pressed state.

The valve plate 2 is formed in a disk shape without irregularities, and as shown in FIG. 4, the suction chamber 31 and the cylinder bore 14 (compression chamber 25) communicate with each other and are opened and closed by a suction valve 51 described below. The suction hole 26, the discharge chamber 32, and the cylinder bore 14 (compression chamber 25) communicate with each other, and discharge holes 27 that are opened and closed by a discharge valve 71 described below are formed at predetermined intervals in the circumferential direction. Further, the valve plate 2 is formed with an orifice hole 45 for forming a part of the extraction passage, a through hole 46 for inserting the fastening bolt 6, a through hole 47 for inserting the positioning pin, and the like. Yes.

As shown in FIG. 2, the suction valve seat 50 is composed of an assembly of a plurality of suction valves 51 that open and close the suction hole 26, and the suction valve seat 50 includes suction valves according to the number of cylinder bores 14. 51 are formed at predetermined intervals in the circumferential direction, and a through hole 52 for inserting the fastening bolt 6, a through hole 53 for inserting the positioning pin, an orifice hole 54 constituting the extraction passage, and the like are formed. Yes. In addition, through holes 56 that avoid interference with the discharge holes 27 are formed at the bases of the respective intake valves 51.

Each intake valve 51 is constituted by a part of the intake valve seat 50, and a U-shaped punching hole 55 is formed in the vicinity of the periphery of the intake valve seat 50 so as to extend integrally inward in the radial direction. It is installed. The suction valve 51 is formed as a reed valve composed of a cantilever beam, and the distal end portion 51 a of the deformation region is a seat portion seated on a seat surface formed around the suction hole 26.

The gasket 60 interposed between the suction valve seat 50 and the cylinder block 1 has through holes 61 that avoid interference with the cylinder bores 14 formed at predetermined intervals in the circumferential direction according to the number of the cylinder bores 14 and are fastened. A through hole 62 for inserting the bolt 6, a through hole 63 for inserting the positioning pin, a through hole 64 for avoiding interference with the extraction passage 43, and the like are formed.

As shown in FIG. 5, the cylinder head 3 is integrally formed with a partition wall 36 formed in an annular shape around the axis of the shaft 110 inside the outer peripheral wall 35. The suction chamber 31 is defined inside the partition wall 36, and the discharge chamber 32 is defined between the partition wall 36 and the outer peripheral wall 35. The end face of the partition wall 36 is formed lower than the end face of the outer peripheral wall 35 by an amount corresponding to the thickness of the discharge valve sheet 70. Further, a bolt screwing seating surface 38 in which a screw hole 37 for screwing the fastening bolt 6 is formed on the inner surface of the outer peripheral wall 35 is integrally bulged toward the discharge chamber 32 (inward in the radial direction). Has been.

The suction chamber 31 is connected to the low-pressure side of the external refrigerant circuit (the outlet side of the evaporator) through a suction passage extending in the radial direction so as to penetrate the annular discharge chamber 32. The discharge chamber 32 communicates with a discharge port 34 (shown in FIG. 2) connected to the high-pressure side of the external refrigerant circuit (inlet side of the radiator).

As shown in FIG. 6, the discharge valve seat 70 is composed of an assembly of a plurality of discharge valves 71 that open and close the discharge holes 27, and the discharge valves 71 are arranged in the circumferential direction according to the number of cylinder bores 14. It is formed at intervals. The discharge valve seat 70 is formed with a through-hole 73 that avoids interference with the orifice hole 45 formed in the valve plate 2 at the center, a through-hole 74 that avoids interference with the suction hole 26 around it, and a positioning pin. A through-hole 72 and the like are formed for inserting the.

Each discharge valve 71 is constituted by a part of the discharge valve seat 70, and is integrally formed on the periphery of a connecting portion 75 that connects adjacent discharge valves. The discharge valve 71 is formed as a reed valve made of a cantilever beam, and the distal end portion 71 a of the deformation region is a seat portion that is seated on a seat surface formed around the discharge hole 27.

In addition, each discharge valve 71 has a distal end portion 71a disposed radially outside the base end portion 71b (the distal end portion 71a is disposed farther from the center O of the discharge valve seat 70 than the base end portion 71b). And are shifted in the circumferential direction. Here, the reference of the radial and circumferential positions is based on the axial center of the compressor, that is, the center of the shaft 7.

In this example, if the pitch circle of the discharge holes 27 arranged around the shaft 7 as a center is C, the axis m of the discharge valve 71 (the center of the distal end portion 71a and the proximal end portion 71b of the discharge valve 71). An imaginary line passing through the center is inclined at a predetermined angle α (30 ° to 60 °) with respect to a tangent t at a portion where the pitch hole discharge hole 27 is provided.

In this example, the width of each discharge valve 71 is gradually reduced from the distal end portion 71a to the proximal end portion 71b. The periphery of the connecting portion 75 that connects the discharge valves is spaced a predetermined distance from the inner edge of the discharge valve 71 from the inner edge of the base end portion 71b of the discharge valve 71 in the width direction. It extends in parallel and is formed so as to be bent from the vicinity of the distal end portion 71a of the discharge valve 71 toward the end portion on the outer side in the width direction of the proximal end portion 71b of the adjacent discharge valve 71.

The partition wall 36 formed in the cylinder head 3 has such a shape that presses the peripheral edge of the connecting portion 75 of the discharge valve seat 70 and the entire width W of the base end portion 71b of the discharge valve 71 (the peripheral edge of the connecting portion 75). The shape is such that the base end portion 71b of the discharge valve 71 overlaps when projected in the axial direction. Further, a partition wall portion 36a that presses the entire width W of the base end portion 71b of the discharge valve 71 is extended so as to be inclined with respect to the radial direction in the vicinity of the bolt screw seat surface 38. The subsequent partition wall portion 36b is bent outward by approximately 90 degrees and extends substantially parallel to the bolt screw seating surface 38.

As shown in FIG. 7, the gasket 80 disposed between the discharge valve seat 70 and the cylinder head 3 matches the shape of the end surface of the outer peripheral wall 35 of the cylinder head 3 and the bolt screw seat surface 38. An annular peripheral edge portion 81 formed, and a connecting portion 82 that is formed in the same shape as the connecting portion 75 of the discharge valve seat 70 inside the annular peripheral edge portion 81 and abuts on the connecting portion 75 of the discharge valve seat 70. Therefore, a retainer 83 that confronts the discharge valve 71 and regulates the lift amount of the discharge valve 71 is integrally formed, and the annular peripheral portion 81 and the connecting portion 82 are integrated through the retainer 83. .

A through hole 84 through which the fastening bolt 6 is inserted is formed in the annular peripheral edge 81 of the gasket 80, and a through hole 87 through which the positioning pin is inserted is formed in the connecting part 82, and the discharge valve The through holes 85 and 86 having the same shape corresponding to the through hole 73 at the center of the sheet 70 and the surrounding through holes 74 are formed.

The retainer 83 is warped so that the distal end portion 83a moves away from the valve plate 2, and the axis n of the retainer 83 (an imaginary line passing through the center of the distal end portion 83a and the center of the proximal end portion 83b of the retainer 83). ) Matches the axis m of the discharge valve 71. In the retainer 83, both side portions 83 c of a portion where the distal end portion 71 a of the discharge valve 71 faces and a portion (base end portion 83 b) where the proximal end portion 71 b of the discharge valve 71 faces each other are connected to the gasket 80. Specifically, the side portion 83c closer to the inner side of the retainer 83 is connected to a peripheral portion 82a that is parallel to the retainer 83 of the connecting portion 82, and the side portion 83c closer to the outer side of the retainer 83 is an annular peripheral portion. The bolt screwing seating surface 81 is connected to a confronting portion 81a.
In this example, the connecting portion 82 disposed on the inner side of the annular peripheral portion 81 of the gasket 80 is formed lower than the annular peripheral portion 81 by an amount corresponding to the thickness of the discharge valve seat 70.

Accordingly, when the position of the through hole 84 of the annular peripheral edge 81 of the gasket 80 is aligned with the screw hole 37 of the bolt threaded seating surface 38 of the cylinder head 3 and the gasket 80 is overlaid on the cylinder head 3, the gasket 80. The entire periphery W of the connecting portion 82 and the width direction W of the base end portion 83 b of the retainer 83 are in contact with the end face of the partition wall 36.

Further, the gasket 80 and the discharge valve seat 70 are aligned with the positions of the through holes (73 and 85, 74 and 86), and the discharge valve 71 is opposed to the retainer 83 so that the peripheral edges of the connecting

portions

75 and 82 And the base end portion 71 b of the discharge valve 71 overlaps with the base end portion 83 b of the retainer 83, and the end surface of the discharge valve seat 70 that faces the valve plate 2 of the annular peripheral portion 81 of the gasket 80. It becomes the same surface as the end surface, and the discharge valve seat 70 is housed inside the gasket 80.

In the configuration described above, the gasket 80 is aligned with the cylinder head 3 at the periphery, and the through hole 84 of the annular peripheral edge 81 of the gasket 80 is aligned with the screw hole 37 of the bolt threaded seating surface 38 of the cylinder head 3. In addition, the discharge valve seat 70 is overlapped with the gasket 80 so that the peripheral edges of the connecting

portions

75 and 82 coincide with each other, and the peripheral edge of the gasket 80 with the discharge valve seat 70 overlapped with the valve plate 2 is aligned. When the

holes

84 and 46 of the fastening bolt 6 are made to coincide with each other, the orifice hole 45 formed in the center of the valve plate 2 is connected to the connecting

portions

75 and 82 of the discharge valve seat 70 and the gasket 80, respectively. The suction hole 26 of the valve plate 2 communicates with the discharge valve seat 70 through the central through

holes

73 and 85 and communicates with the suction chamber 31. The discharge hole 27 of the valve plate 2 communicates with the suction chamber 31 via the through

holes

74 and 86 formed in the vicinity of the peripheral edges of the connecting

portions

75 and 82 of the sket 80, and the distal end portion 71 a of the discharge valve 71 is formed at the peripheral edge. It will be in the state closed by contact.

The discharge valve 71 has a distal end portion 71a disposed radially outside the proximal end portion 71b and the distal end portion 71a is disposed so as to be shifted in the circumferential direction with respect to the proximal end portion 71b. The refrigerant gas opened and discharged is guided in the direction opposite to the base end portion 71 b of the discharge valve 71, that is, the direction in which the tip end portion 71 a of the discharge valve 71 is directed, and along the circumferential direction of the annular discharge chamber 32. It will flow smoothly.

In addition, the distal end portion 71a of the discharge valve 71 is inclined outward with respect to the circumferential direction of the cylinder head 3, and the proximal end portion 71b of the discharge valve 71 is disposed closer to the center of the cylinder head 3, so that the discharge valve The base end portion of the retainer 83 and the base end portion 83 b of the retainer 83 are pressed and fixed to the valve plate 2 by a partition wall 36 that partitions the discharge chamber 32 and the suction chamber 31 in the entire width direction W.
As a result, there is no inconvenience that twisting occurs when the discharge valve 71 is opened, and the possibility of damage to the discharge valve can be eliminated. Further, since it is not necessary to make the discharge valve seat 70 large and clamp it on the outer peripheral wall 35 of the cylinder head 3, it is possible to reduce the cost of parts.

Further, in the above-described configuration, the portion of the gasket 80 adjacent to both side portions 83 c of the retainer 83 includes the end surface of the partition wall 36 and the bolt screw seat surface 38 that is formed to bulge inward from the outer peripheral wall 35 of the cylinder head 3. (The portion 82a of the gasket 80 adjacent to the inner side portion 83c of the retainer 83 is pressed and fixed to the valve plate 2 by the end face of the partition wall 36, and the outer side of the retainer 83 is fixed to the valve plate 2. The portion 81a of the gasket 80 adjacent to the portion 83c is pressed and fixed to the valve plate 2 by the bolt screw seating surface 38).

In this way, the discharge valve 71 is not disposed in the radial direction or the circumferential direction of the cylinder head 3 but is disposed so as to be inclined so that the tip end portion 71a faces outward with respect to the tangential direction (discharge valve 71). Since the distal end portion 71a of the discharge valve 71 is disposed radially outward from the proximal end portion 71b and shifted in the circumferential direction), the proximal end portion 71b of the discharge valve 71 can be disposed closer to the center of the cylinder head 3. The entire area W in the width direction of the base end portion 71 b of the discharge valve 71 can be easily pressed and fixed to the valve plate 2 by the partition wall 36.

In addition, in order to press the base end portion 71 b of the discharge valve 71, it is necessary to enlarge the bolt threaded seating surface 38 bulging inward from the outer peripheral wall 35 of the cylinder head 3, or the discharge chamber 32 and the suction chamber 31. Therefore, it is not necessary to place the partition wall 36 that is extremely close to the outer peripheral wall 35 of the cylinder head 3, and it is possible to avoid the disadvantage that the width of the discharge chamber 32 (discharge gas passage width) becomes unnecessarily narrow.

In the above-described example, the width of the discharge valve 71 is gradually reduced from the distal end portion 71a to the proximal end portion 71b, so that the necessary width of the proximal end portion 71b to be pressed can be shortened by the partition wall 36. The entire base end portion can be more reliably pressed, and the width of the base end portion 71b to be pressed by the partition wall 36 is shortened, so that a large width of the discharge chamber 32 (discharge gas passage width) can be secured. It becomes possible.

Further, a portion of the gasket 80 adjacent to both side portions 83c of the retainer 83 provided in the gasket 80 is formed with an end surface of the partition wall 36 and a bolt threaded seating surface 38 bulging inward from the outer peripheral wall 35 of the cylinder head 3. Therefore, it is not necessary to use the outer peripheral wall 35 of the cylinder head 3 to press the portion of the gasket 80 adjacent to the side of the retainer 83, and the wall thickness of the outer peripheral wall 35 can be reduced. Can be made thinner. As a result, the outer diameter and weight of the cylinder head 3 can be reduced, and the compressor can be reduced in size and weight.

Furthermore, in the above-described configuration example, since the peripheral edge of the connecting portion 75 that connects the discharge valves 71 of the discharge valve seat 70 is also pressed and fixed to the valve plate 2 by the partition wall 36, the fixed state of the discharge valve 71 is further strengthened. Therefore, a more stable opening / closing operation of the discharge valve 71 can be ensured. S

DESCRIPTION OF SYMBOLS 1 Cylinder block 2 Valve plate 3 Cylinder head 14 Cylinder bore 15 Piston 26 Suction hole 27 Discharge hole 31 Suction chamber 32 Discharge chamber 36 Bulkhead 38 Bolt screwing seat surface 71 Discharge valve 75 Connection part 80 Gasket 83 Retainer

Claims

A cylinder block in which a plurality of cylinder bores for reciprocally accommodating a piston are arranged around the shaft;
A valve plate provided at an end of the cylinder block and having a suction hole and a discharge hole corresponding to each cylinder bore;
A suction chamber that is assembled to the cylinder block with the valve plate interposed therebetween and communicates with each of the suction holes; and a discharge chamber that communicates with each of the discharge holes. A cylinder head formed in a portion, and the discharge chamber formed in an annular shape around the suction chamber;
A reed valve type intake valve that is provided on the cylinder block side of the valve plate and opens and closes the intake hole;
A reed valve type discharge valve provided on the cylinder head side of the valve plate for opening and closing the discharge hole;
A reciprocating compressor that draws refrigerant gas in the suction chamber into the cylinder bore through the suction hole and discharges the compressed refrigerant gas to the discharge chamber through the discharge hole by reciprocation of the piston. In
The discharge valve is arranged with its distal end disposed radially outward from the proximal end and shifted in the circumferential direction,
A reciprocating compressor, wherein a base end portion of the discharge valve is pressed and fixed to the valve plate by a partition wall that partitions the discharge chamber and the suction chamber.
The reciprocating compressor according to claim 1, wherein a width of the discharge valve is gradually reduced from the distal end portion to the proximal end portion.
The discharge holes are arranged on a pitch circle centered on the shaft, and the axis of the discharge valve is 30 degrees to 60 degrees with respect to a tangent at a portion of the pitch circle where the discharge holes are provided. The reciprocating compressor according to claim 1, wherein the reciprocating compressor is inclined in a range of
A gasket is interposed between the discharge valve and the valve plate, and a retainer for restricting a lift amount of the discharge valve is formed integrally with the gasket so as to face the discharge valve. The discharge valve of the retainer The both sides of the portion where the tip of the discharge valve faces and the portion where the base end of the discharge valve faces are connected to the gasket,
The portion of the gasket adjacent to the both side portions of the retainer is pressed and fixed to the valve plate by an end surface of the partition wall and a bolt screw seat surface formed to bulge inward from the outer peripheral wall of the cylinder head,
The reciprocating compression according to any one of claims 1 to 3, wherein a base end portion of the retainer and a base end portion of the discharge valve are overlapped and pressed against the valve plate by the partition wall. Machine.
Each discharge valve corresponding to the plurality of cylinder bores is formed integrally with a discharge valve forming plate, and the peripheral edge of the connecting portion connecting the discharge valves of the discharge valve forming plate is pressed against the valve plate by the partition wall. The reciprocating compressor according to any one of claims 1 to 4, wherein the compressor is fixed.