JP2001032774A - Valve device of reciprocating coolant compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce stress generated in a suction valve to realize excellent durability by inserting a spacer made of elastic body of thin plate between the head part of a fastening means and the suction valve, and fastening the spacer, the suction valve and a valve seat plate in this order. SOLUTION: A spacer 24 of an annular thin plate type is fastened so as to be sandwiched between a rivet head 17a and a suction valve 11 by a rivet 17 in order of the spacer 24, the suction valve 11 and a valve seat plate 9. The suction valve 11 start displacement by a blowout force of coolant sucked by suction port 10, and a suction valve claw comes into contact with a suction valve stopper 23 provided in a cylinder bore opening whereby a suction valve arm part 11a is displaced to be a curved shape. At this time, since the spacer 24 inserted between the rivet 17 and the suction valve 11 has elasticity, the spacer 24 displaces while following the suction valve 11. An inflection point of the suction valve 11 is dispersed to a two point, that is, an outer peripheral part of the rivet head 17a and an outer peripheral part of the spacer 24, and the maximum stress generated in an outer diameter part corresponding to a head of fastening means of the suction valve 11 is reduced. Further, addition of the spacer 24 enables coping with changes such as solvent change.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve device for a reciprocating refrigerant compressor having a structure in which a suction valve and a valve seat plate are integrally fastened.

[0002]

2. Description of the Related Art As prior art of the present invention, for example,
The technology of JP-A-7-44991 is known. FIG. 10 shows a sectional view of a main part of a conventional valve device of this type. 1 is a crankshaft that performs eccentric motion, 2 is a connecting rod that converts the rotational motion of the crankshaft 1 into reciprocating motion, 3 is a cast cylinder block, 4 is a cylinder bore, 5 is a piston that performs reciprocating motion inside the cylinder bore 4, Reference numeral 6 denotes a pair of left and right arc-shaped ridges having the same trapezoidal cross section as a discharge port described later projecting from the top surface of the piston. Reference numeral 7 denotes a cylinder head that covers a valve device 18 described later and is bolted to the cylinder block 3.
8 is an end face of the cylinder head 7 and the cylinder block 3.
The gasket 9 seals the top of the cylinder bore 4 and has a suction port 10 described later and a discharge port 12 described later.
Is a suction port provided on a valve seat plate 9 which is provided on an outer peripheral surface of an opening of the cylinder bore 4 and communicates with a suction chamber 20 described later, and 11 is an annular ring with an arm for opening and closing the suction port. A suction valve (hereinafter abbreviated as a suction valve), 12 is a pair of left and right discharge ports formed in an arc shape on both sides of the center of the valve seat plate 9, and 13 is provided on the upper surface of the valve seat plate 9 to open and close the discharge port. The set discharge valve 14 regulates the movement of the discharge valve 13 and presses against the valve seat plate 9.
3. A valve retainer that houses and holds the valve spring 14 and the sheet valve 16 in the inner peripheral groove.

[0003] The suction valve 11 penetrates through the center hole of the valve seat plate 9 and the valve retainer 15, and is provided on the cylinder bore 4 side of the valve seat plate 9.
A rivet, which is a fastening means that constitutes a valve device by fastening a valve retainer 15 in which a discharge valve 13 and a valve spring 14 are housed and held in an inner peripheral groove portion on the cylinder head 7 side, and a rivet 18 is integrally fixed by a rivet, A valve device pressed and fixed to the opening of the cylinder bore 4 by the cylinder head 7 via a spring 19; a suction chamber 20 filled with low-pressure refrigerant gas; a discharge chamber 21 surrounded by the cylinder head 7 and the valve device 18; Reference numeral 22 denotes an o-ring mounted on the outer peripheral portion of the valve seat plate 9 for sealing the discharge chamber 21 and the suction chamber 20.
Reference numeral 3 denotes a notched suction valve stopper formed at the upper end of the cylinder bore 4 for restricting the valve lift of the suction valve 11.

Next, the operation will be described. The piston 5 is a crankshaft 1 that is eccentrically rotated by an electric motor (not shown).
And the connecting rod 2 reciprocates. When the pressure in the space (cylinder) closed by the valve device 18, the piston 5 and the cylinder bore 4 becomes lower than the pressure in the suction chamber 20 when the piston 5 descends, the suction valve 11 opens and refrigerant gas is sucked into the cylinder. Next, when the piston 5 rises, the refrigerant gas is compressed in the cylinder and becomes a high pressure, passes through the discharge port 12 of the valve seat plate 9, pushes up the discharge valve 13, and pushes the discharge chamber 2 upward.
Is discharged to 1. As a result, the discharge valve 13 and the suction valve 11 repeat opening and closing for each reciprocation of the piston 5.

FIG. 11 is a plan view of the suction valve 11, and FIG. 12 is a longitudinal sectional view in the arm direction showing a state of deformation of the suction valve 11 during a suction process. 11 and 12, 11b is a suction valve claw portion, 11a is a suction valve arm portion, and 11c is a suction valve 11
Shows the rivet head outer diameter phase head, which is a fastening means in the arm direction, and when the suction valve 11 starts to open, the suction valve claw 1
1b comes into contact with a suction valve stopper 23 provided at the opening of the cylinder bore 4, and furthermore, the output of the refrigerant gas passing through the valve seat plate 9 (indicated by an arrow in the drawing) causes the suction valve arm 1
1a is curved, and a maximum stress acts on the rivet head outer diameter phase head 11c as a fastening means.

[0006]

In the conventional structure, when the operating pressure range is increased due to a change in refrigerant or the like, the maximum stress of the suction valve increases, so that the plate thickness is increased, the valve lift is reduced, and the rigidity is increased. It is necessary to change to valve material, etc.
Since the impact sound at the time of opening and closing the suction valve increases, the performance decreases due to the delay of the opening and closing of the suction valve, and the compression efficiency decreases, it is necessary to newly design and manufacture the material, thickness, shape, etc. The cost could not be increased and the cost was up. In the conventional method of caulking a rivet by pressurization, the valve device components rotate loose due to uneven plastic deformation of the rivet and poor caulking due to aging of the jig, and the suction valve interferes with the piston and abnormal noise occurs. And the pressurizing jig deteriorates and cannot be securely fixed. Also,
In the case of caulking by the current welding method, there has been a problem that the allowable stress is reduced due to the burning of the suction valve due to local heat and the residual stress.

The present invention has been made in view of the above, and even if the working pressure range is increased due to a change in refrigerant or the like, the compression efficiency can be improved without changing the material, shape, and valve lift of the conventional suction valve. It is another object of the present invention to provide an inexpensive valve device which has low noise, improves the strength of a suction valve, and has excellent durability.

Further, according to the present invention, the rivet is caulked by using a current welding method, and the valve device is securely fastened in a short time, thereby reducing burn-in of the suction valve and residual stress during current welding, thereby reducing the defective rate. It is intended to provide a valve device.

[0009]

According to a first aspect of the present invention, there is provided a valve device for a reciprocating refrigerant compressor, wherein an intake valve and a valve seat plate are axially overlapped and integrally formed by fastening means. In the apparatus, a spacer made of a thin elastic material is inserted between the head of the fastening means and the suction valve, and a spacer is provided by the fastening means.
The suction valve and the valve seat plate are fastened in this order.

In the valve device according to the second aspect of the present invention, the outer diameter of the spacer is larger than the outer diameter of the head of the fastening means.
In addition, the outer diameter of the center portion of the arm-shaped annular suction valve having the arm portion and the center portion is set to be equal to or less than the outer diameter.

Further, in the valve device according to the third aspect of the present invention, the thickness of the spacer is selected so that the stresses of the suction valve and the spacer corresponding to the outer diameter portion of the fastening means head portion are substantially the same. Things.

The valve device according to a fourth aspect of the present invention uses a rivet as a fastening means and is caulked by a current welding method.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view of a main part of a valve device according to the present invention, and FIG. 2 is an exploded perspective view of components of the valve device. 1 is a crankshaft that performs eccentric motion, 2 is a connecting rod that converts the rotational motion of the crankshaft 1 into reciprocating motion, 3 is a cast cylinder block, 4 is a cylinder bore,
Reference numeral 5 denotes a piston which reciprocates inside the cylinder bore 4, reference numeral 6 denotes a pair of left and right arc-shaped projections having the same trapezoidal cross section as a discharge port 12 described later projecting from the top surface of the piston, and reference numeral 7 denotes a valve device described later. Cover cylinder 18 and cylinder block 3
8 is a gasket that seals the end faces of the cylinder head 7 and the cylinder block 3, 9 seals the top of the cylinder bore 4, and forms a suction port 10 described below and a discharge port 12 described below. The valve seat plate 10 made of sintered metal is a suction port provided on a valve seat plate 9 which is provided on the outer peripheral surface of the opening of the cylinder bore 4 and communicates with a suction chamber 20 described later, and 11 is a suction valve for opening and closing the suction port. In this embodiment, an annular suction valve with an arm is shown. 12 is a pair of left and right discharge ports formed in an arc shape on both sides of the center of the valve seat plate 9, 13 is a strip steel discharge valve provided on the upper surface of the valve seat plate 9 to open and close the discharge ports, and 14 is Discharge valve 1
Reference numeral 15 denotes a valve spring that regulates the movement of the valve 3 and presses it against the valve seat plate 9. Reference numeral 15 denotes a sintered alloy valve retainer that accommodates and holds the discharge valve 13, the valve spring 14, and the sheet valve 16 in the inner peripheral groove.

Reference numeral 17 passes through the central hole of the valve seat plate 9 and the valve retainer 15, and the suction valve 11 is provided on the cylinder bore 4 side of the valve seat plate 9.
A rivet, which is a fastening means for integrally forming a valve retainer 15 having a discharge valve 13 and a valve spring 14 housed and held in an inner peripheral groove portion on the cylinder head 7 side to constitute a valve device; 17a, a rivet head; Is a valve device which is fastened by rivets and is pressed and fixed to the opening of the cylinder bore 4 by the cylinder head 7 via a disc spring 19, 20 is a suction chamber filled with low-pressure refrigerant gas, 21 is the cylinder head 7 and the valve device 18
A discharge chamber 22 is formed by sealing the discharge chamber 21 and the suction chamber 20 so as to seal the discharge chamber 21 and the suction chamber 20. An orifice 23 is formed at the upper end of the cylinder bore 4. , A notch-shaped suction valve stopper for regulating the valve lift of the suction valve 11. Reference numeral 24 denotes a spacer, which is formed in an annular thin plate shape in this embodiment.
The spacer 24 is fastened so as to be sandwiched between the rivet head 17a and the suction valve 11 by the rivet 17 as fastening means in the order of the valve seat plate 9.

FIG. 3 is a plan view of the suction valve stopper 23. Reference numeral 23a denotes an arm-direction stopper, and reference numeral 23b denotes a right-angle stopper provided substantially perpendicular to the arm-direction stopper 23a. The suction valve 11 has an annular shape with an arm as shown in FIGS. 2 and 4, 11a represents an arm, 11b represents a claw, and 11e represents a center. The rigidity in the arm direction is higher than that in the right angle direction. Therefore, considering the rigidity ratio between the arm direction and the right angle direction, the arm direction corresponding depth 23a and the right angle direction depth 23a of the suction valve stopper 23 are reduced so that the lift amount in the arm direction is reduced.
b is set.

Next, the operation will be described. The piston 5 is a crankshaft 1 that is eccentrically rotated by an electric motor (not shown).
And the connecting rod 2 reciprocates. When the pressure in the space (cylinder) closed by the valve device 18, the piston 5 and the cylinder bore 4 becomes lower than the pressure in the suction chamber 20 when the piston 5 descends, the suction valve 11 opens and refrigerant gas is sucked into the cylinder. Next, when the piston 5 rises, the refrigerant gas is compressed in the cylinder and becomes a high pressure, passes through the discharge port 12 of the valve seat plate 9, pushes up the discharge valve 13, and pushes the discharge chamber 2 upward.
Is discharged to 1. As a result, the discharge valve 13 and the suction valve 11 repeat opening and closing for each reciprocation of the piston 5.

FIG. 4 is a plan view showing the maximum displacement position of the suction valve 11. Since the suction valve lift is set to be larger in the right angle direction than in the arm direction, the suction valve 11 undergoes the maximum displacement at 11d. .

FIG. 5 is a vertical sectional view in the arm direction showing the lift of the suction valve 11 in the suction stroke of the valve device 18. The suction valve 11 starts to be displaced by the ejection power of the refrigerant sucked from the suction port 10. The suction valve claw 11b comes into contact with the suction valve stopper 23 provided at the opening of the cylinder bore 4, and the suction valve arm 11a is deformed into a curved shape. At this time, since the spacer 24 inserted between the rivet 17 and the suction valve 11 has elasticity, the spacer 24 is displaced following the suction valve 11, and the inflection point of the displacement of the suction valve 11 is determined by the conventional valve device. The rivet 17 head 17
The maximum stress value which is distributed at two places, that is, the outer peripheral part of the suction valve 11 and the outer peripheral part of the spacer 24, is reduced in the outer diameter part 11c corresponding to the head of the fastening means of the suction valve 11. Therefore, the refrigerant used is R2
When the operating pressure condition becomes severe (for example, when the saturation pressure at the same operating temperature is higher than R22 at R407C and R410A), such as when changing from 2 to R407C or R410A, the conventional suction valve is used as it is. If used, the stress of the suction valve would increase and the reliability would decrease, so specification changes were required. However, in the present invention, the suction pressure was changed simply by adding a spacer to the conventional suction valve and adding a spacer (for example, changing refrigerant). ) Can also be handled.

Therefore, even if the working pressure range becomes large due to a change in refrigerant or the like, the stress generated in the suction valve can be reduced without changing the material, shape and valve lift of the conventional suction valve, so that the valve device is excellent in durability. Can be provided. In addition, since the suction valve can be shared with the conventional product, the suction valve can be manufactured at a lower cost than when a new suction valve is developed and the plate thickness is changed. Further, since the displacement of the suction valve is hardly changed, the flow path resistance is the same, the compression efficiency does not decrease, and the noise does not increase. In this embodiment, the shape of the spacer is an annular thin plate. However, the spacer need not be annular and may be any thin elastic plate. Further, in this embodiment, only one spacer is used for the suction valve. However, the same effect can be obtained by overlapping several spacers.

Embodiment 2 Embodiment 2 of the present invention will be described with reference to FIGS. The suction valve 11 is an annular suction valve with an arm, and the spacer 24 has an outer diameter equal to or smaller than the outer diameter of the central portion 11e of the annular suction valve with an arm 11 and larger than the head 17a of the rivet 17 as a fastening means. I have. FIG.
Is the maximum displacement and the maximum of the annular suction valve 11 with the arm when the outer diameter of the spacer 24 is changed by setting the outer diameter of the head 17a of the rivet 17 to 7 mm and the outer diameter of the central portion 17e of the suction valve 11 to 14 mm. It is a graph showing stress. In the figure, the horizontal axis represents the outer diameter of the spacer, and the vertical axis represents the stress ratio and the displacement ratio when the case where there is no spacer 24 is set to 1.

As shown in FIG. 8, the maximum stress generated in the arm-shaped annular suction valve 11 is such that the outer diameter of the spacer 24 is
Rivet 1 which is fastening means below the outer diameter of the central portion 11e of the rivet 1
It can be seen that the minimum value is obtained within a range larger than the head 17a of No. 7. Further, since the maximum displacement is almost the same as the case without the spacer 24, the flow path resistance is considered to be almost the same, so that the compression efficiency does not decrease due to an increase in the suction pressure loss. Therefore, by forming the spacer 24 with an outer diameter smaller than the outer diameter of the center portion 11e of the annular suction valve 11 with arms and larger than the head 17a of the rivet 17 as a fastening means, the displacement amount is hardly changed. Since the stress can be reduced, even if the working pressure range is increased by changing the refrigerant, the stress generated in the suction valve can be reduced without changing the material, shape, and valve lift of the conventional suction valve, resulting in durability. In addition, it is possible to provide a valve device which is excellent in quality, and the common use of a suction valve with a conventional product can be achieved. Further, since the displacement of the suction valve is hardly changed, the flow path resistance is the same, the compression efficiency does not decrease, and the noise does not increase.

In this embodiment, rivets are used for caulking the valve device. However, similar effects can be obtained by tightening with a bolt and a nut. The same effect can be obtained by using a ring-shaped suction valve other than the arm-shaped suction valve.

Embodiment 3 FIG. An example of the third embodiment of the present invention will be described. The spacer 24 has a thickness that does not hinder the bending motion of the suction valve 11 and is formed by pressing a thin steel strip having the same thickness as that of the suction valve by press punching. After that, it is fixed by rivet caulking. FIG.
The maximum stress generated in the arm-shaped annular suction valve 11 and the spacer 24 when the plate thickness is changed according to the third embodiment of the present invention will be described. FIG. 9 is a graph showing the maximum stress generated in the annular suction valve with arm 11 and the spacer 24 when the plate thickness of the spacer 24 is changed. In the figure, the horizontal axis represents the ratio of the thickness of the spacer 24 to the thickness of the suction valve 11,
The vertical axis represents the stress ratio when the case where there is no spacer 24 is set to 1. From FIG. 9, when the plate thickness of each of the arm-shaped annular suction valve 11 and the spacer 24 is made substantially the same, the maximum stress of both the arm-shaped annular suction valve 11 and the spacer 24 is substantially the same, and when there is no spacer 24. It can be seen that a significant reduction is possible. (In the figure, when the thickness ratio of the spacer is 1, the stress is the same for both the suction valve and the spacer, and the stress is reduced to 60%.)

FIGS. 6 and 7 show the results obtained by FEM analysis of the maximum stress value and the maximum displacement amount of the suction valve 11 with the spacer 24 when the lift amount in the arm direction is changed. This is a graph in which the case is set to 1.

FIG. 6 shows the spacer 2 of the present invention when the lift amount of the suction valve 11 is set to 1 when there is no spacer 24 on the horizontal axis.
The vertical axis indicates the ratio of the lift amount in the case where
The ratio in the case where the spacer 24 of the present invention is present is shown assuming that the maximum generated stress value generated in the suction valve in the case where there is no spacer is 1. As a result, the suction valve with the spacer has the same structure as the case without the spacer, even if the lift in the arm direction is increased.
It can be seen that the maximum stress value ratio with respect to the case where there is no 4 is hardly changed and is always about 60%, which is reduced.

FIG. 7 shows the spacer 2 according to the present invention when the lift amount of the suction valve 11 is set to 1 when there is no spacer 24 on the horizontal axis.
The ratio in the case where there is the spacer 24 of the present invention is shown with the maximum displacement amount generated in the suction valve 11 in the case where there is no spacer 24 on the vertical axis as 1. From this, it can be understood that the maximum displacement of the suction valve with the spacer is equal to that in the case where there is no spacer at any lift amount, so that the pressure loss and the compressor input due to the reduction of the suction passage do not occur. .

Therefore, the annular suction valve with arm 11 and the spacer 2
Since the plate thickness of No. 4 is the same, the stress generated in the suction valve can be reduced without changing the material, shape, and valve lift of the conventional suction valve even if the operating pressure range becomes large due to a change in refrigerant or the like. It is possible to provide a valve device having excellent durability, and the common use of the suction valve with the conventional product can be achieved. Therefore, it can be manufactured at a lower cost than when a new suction valve is newly developed and the thickness is changed. Further, since the displacement of the suction valve is hardly changed, the flow path resistance is the same, the compression efficiency does not decrease, and the noise does not increase. Further, since the same thickness of the spacer 24 as that of the arm-shaped annular suction valve 11 can be used, the same material can be used. In the case where the arm-shaped annular suction valve 11 is manufactured by pressing, for example, the spacer 24 is manufactured by using waste material after pressing. It is also possible and can be inexpensive.

Embodiment 4 A rivet is used as the fastening means 17, a spacer 24 made of a thin elastic material is inserted between the rivet head 17a and the suction valve 11, and both ends of the rivet are pressurized, a voltage is applied, a current is applied, and a local current is applied. It is caulked by the current welding method of melting and welding. Therefore, the valve device can be securely fixed in a short time. Further, since the melting and welding are locally performed, the suction valve 11 is not deformed and a highly reliable valve device can be provided. Furthermore, since the spacer is inserted and caulked by the current welding method, the residual stress generated in the suction valve burn and the suction valve during current welding can be reduced as compared with the case without the spacer, and the defective rate can be reduced. .

[0029]

The valve device according to the first invention of the present invention is a valve device for a reciprocating refrigerant compressor in which a suction valve and a valve seat plate are axially overlapped and fastened by fastening means. A spacer made of a thin elastic material is inserted between the head and the suction valve, and the spacer, the suction valve, and the valve seat plate are fastened in this order by the fastening means. The stress generated in the suction valve can be reduced without changing the material, shape, and valve lift of the conventional suction valve, so that a valve device with excellent durability can be provided, and the displacement of the suction valve is hardly changed. Therefore, the flow path resistance is the same and the compression efficiency does not decrease.

In the valve device according to the second aspect of the present invention, the outer diameter of the spacer is larger than the outer diameter of the head of the fastening means.
In addition, since the outer diameter of the center portion of the arm-shaped annular suction valve having the arm portion and the center portion is equal to or less than the center portion, the generated stress can be reduced without substantially changing the displacement amount of the suction valve. Even if it gets bigger, the material, shape,
Since the stress generated in the suction valve can be reduced without changing the valve lift, a valve device having excellent durability can be provided.

In the valve device according to the third aspect of the present invention, since the thickness of the spacer is selected so that the stress of the suction valve and the spacer at the portion corresponding to the outer diameter portion of the fastening means head is substantially the same, Even if the operating pressure range becomes large due to refrigerant change, etc., the stress generated in the suction valve can be reduced without changing the material, shape and valve lift of the conventional suction valve, so that the conventional product and the suction valve can be shared, It can be manufactured at lower cost than when a new suction valve is developed and the plate thickness is changed. In addition, the same material as the annular suction valve with arm can be used for the thickness of the spacer, so the material can be the same, and when manufacturing the annular suction valve with arms by pressing, it is possible to manufacture with waste material after pressing And the spacer can be made inexpensive.

In the valve device according to the fourth aspect of the present invention, a rivet is used as the fastening means, and a spacer is inserted between the head of the fastening means and the suction valve and caulked by current welding. Since the suction valve burn and residual stress generated by the excessive welding heat can be reduced, a highly reliable valve device can be provided.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a main part of a valve device according to the present invention.

FIG. 2 is an exploded perspective view of components of the valve device according to the present invention.

FIG. 3 is a plan view showing a suction valve stopper according to the present invention.

FIG. 4 is a plan view showing the maximum displacement position of the suction valve according to the present invention.

FIG. 5 is an arm sectional view showing the deformation of the suction valve during the suction stroke of the valve device according to the present invention.

FIG. 6 is a graph showing a relationship between a lift amount of a suction valve and a maximum stress value generated in an arm-direction caulking portion of the conventional valve device and the valve device of the present invention.

FIG. 7 is a graph showing a relationship between a suction valve lift amount and a suction valve maximum displacement amount of a conventional valve device and the valve device of the present invention.

FIG. 8 is a graph showing a relationship between a spacer diameter and a maximum stress and a maximum displacement according to the present invention.

FIG. 9 is a graph showing a relationship between a spacer thickness and a stress according to the present invention.

FIG. 10 is a sectional view of a main part showing a conventional valve device.

FIG. 11 is a plan view showing an annular suction valve with an arm.

FIG. 12 is a cross-sectional view in an arm direction showing a deformation of a suction valve in a suction stroke of a conventional valve device.

[Description of Signs] 1 crankshaft, 2 connecting rod, 3 cylinder block, 4 cylinder bore, 5 piston, 6 arc-shaped ridge, 7 cylinder head, 8 gasket, 9 valve seat plate, 10 suction port, 11 suction valve, 11a suction valve arm portion, 11b suction valve claw portion, 11c fastening device head outer diameter equivalent portion, 11d suction valve maximum displacement portion, 11e suction valve central portion outer diameter, 12 discharge port, 13 discharge valve, 14 valve spring , 15 valve retainer, 16 sheet valve, 17 rivet as fastening means, 17a rivet head, 18 valve device, 19 disc spring, 20 suction chamber, 21 discharge chamber, 22
O-ring, 23 suction valve stopper, 23a arm direction suction valve stopper, 23b right angle direction suction valve stopper, 2
4 Spacer

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Hattori required F-term (reference) 3-2, Otemachi 2-chome, Chiyoda-ku, Tokyo 3H003 AA02 AC03 CC11 CC12 CE01 3H058 AA15 BB22 BB29 BB34 BB37 CD06 CD23 EE05 EE09 EE13 EE17

Claims (4)

[Claims] 1. A reciprocating refrigerant compressor having a valve device having a valve device fastened by fastening means, wherein a valve seat plate having a suction port for sucking refrigerant gas and a suction valve for opening and closing the suction port are axially overlapped. A spacer made of a thin elastic material is inserted between the head of the fastening means and the suction valve, and the spacer, the suction valve, and the valve seat plate are fastened in this order by the fastening means. Valve device. 2. The suction valve is an arm-shaped annular suction valve having an arm portion and a center portion. The outer diameter of the spacer is larger than the outer diameter of the head of the fastening means, and the outer diameter of the center portion of the arm-shaped annular suction valve. The valve device according to claim 1, wherein: 3. The spacer according to claim 1, wherein the thickness of the spacer is selected so that the respective stresses of the suction valve and the spacer at the portion corresponding to the outer diameter portion of the fastening means head are substantially the same. The described valve device 4. The valve device according to claim 1, wherein a rivet is used as the fastening means, and the rivet is swaged by a current welding method.