JP3430486B2 - Reciprocating compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor, and more particularly to an improvement of a suction valve mechanism in a variable capacity reciprocating compressor which makes a compression capacity of a refrigerant variable.

[0002]

2. Description of the Related Art Conventionally, as a compressor for vehicle air conditioning for circulating a cooling gas serving as a refrigerant in an air conditioning system, for example, as shown in FIG. 1, a compression force is obtained by reciprocating movement of a piston. A reciprocating type reciprocating compressor (hereinafter, simply referred to as a compressor) 101 is known. This compressor 101 is of a variable capacity type that makes the suction capacity of the cooling gas variable, and a plurality (for example, seven) is provided.
Equipped with a piston.

As shown in FIG. 1, a compressor 101 is assembled with a front housing 103, a cylinder block 104, a cylinder head 105, a valve plate 106, etc., so that a compressor casing 102 as a casing serving as a pressure container is provided. It is formed.

In the compressor casing 102, a cylinder gasket and a head gasket are attached as sealing materials at the joint between the cylinder block 104 and the valve plate 106 and at the joint between the cylinder head 105 and the valve plate 106, respectively. In FIG. 1, the cylinder gasket 10 between the cylinder block 104 and the valve plate 106 is shown for convenience.
Only 7 is shown.

Inside the compressor casing 102,
The drive shaft 108 rotatably stored, and the drive shaft 108.
A plurality of pistons 110 and the like that reciprocate in the cylinder block 104 by the rotation of are arranged.

That is, in the compressor casing 102, through holes 111 and 112 for supporting the drive shaft 108 are formed in the center of the front housing 103 and the center of the cylinder block 104. The drive shaft 108 is rotatably attached to the holes 111 and 112 via bearings 113 and 114, a drive shaft support member 115, and the like.

Around the through hole 112 of the cylinder block 104, there are provided as many cylinders 116 as the number of pistons 110 for accommodating the pistons 110. Each of the cylinders 116, as shown in FIG.
The piston 110 is formed so as to reciprocate in parallel with the axial direction of the drive shaft 108. Compressor casing 102
Then, the space below the through hole portion 112 and the cylinder 116 (on the left side in the drawing) is the crank chamber 117,
The drive shaft 108 rotates in the crank chamber 117, and the swing plate 122 described below swings accordingly.

A rotor 118 is fixed to the drive shaft 108 by a rotor rotation stopping pin 119, and the swash plate boss 12 is attached to the rotor 118.
1 is connected. A swing plate 122 is attached to the swash plate boss 121, and the swing plate 122 is
It is connected to each piston 110 via a piston rod 123 by a universal joint (universal joint) method.

Specifically, the rotor 118 and the swash plate boss 121 have ears 124 and 125, respectively, and the engaging pin 124a provided on the ears 124 on the rotor 118 side has a swash plate boss 121. The ear portion 125 on the side is movably engaged with the long hole portion 125a formed in a predetermined size, so that the connection is achieved by a so-called hinge mechanism.

Further, the rocking plate 122 is the bearing 1
It is attached to the swash plate boss 121 via 26 and 127 so as to be rotatable relative to the swash plate boss 121. As a result, the swing plate 122 does not rotate with the rotation of the swash plate boss 121.

On the other hand, the valve plate 106 is located inside the compressor casing 102 so as to be sandwiched between the cylinder block 104 and the cylinder head 105 by screwing. In the valve plate 106, suction holes 131 for sucking the cooling gas into the cylinder 116 and discharge holes 132 for discharging the cooling gas in the cylinder 116 to the outside are formed by the number of pistons 110. A spring-shaped suction valve member 129 and a discharge valve member 133 are attached to the valve plate 106 so as to close the suction hole 131 and the discharge hole 132.

Here, the intake valve member 129 is mounted on the main surface of the valve plate 106 on the side facing the cylinder block 104, and the details will be described later, but the number of pistons 110 and cylinders 116 (in this case, seven). Only the intake valve is formed. Then, the intake valve member 129 is moved (amount of movement) by contacting the tip end portion of each intake valve with a valve receiving portion (recess) 134 which is a notch groove formed on the upper end side of each cylinder 116 in the cylinder block 104. The amount of lift) is limited.

On the other hand, the discharge valve member 133 is mounted on the main surface of the valve plate 106 facing the cylinder head 105, and seven discharge valves are formed. This discharge valve member 1
On the upper side of 33, a discharge valve receiving member 135 that has the same planar shape as the discharge valve member 133 and limits the lift amount of each discharge valve is attached.

The cylinder head 105 has a substantially bowl shape,
A partition wall 141 for partitioning a space is formed inside thereof. That is, in the cylinder head 105, the internal space is defined by the partition wall 141 so that the suction chamber 142 and the discharge chamber 14 are separated.
It is separated into 3. Here, the suction chamber 142 is the valve plate 1
No. 06 suction hole 131, and the suction valve member 1
Flow paths of the cooling gas to the plurality of cylinders 116 are formed through the 29 suction valves.

The discharge chamber 143 is provided with the discharge valve member 1 described above.
33 through the discharge hole 132 of the valve plate 106,
A plurality of cylinders 1 through each discharge valve of the discharge valve member 133.
It serves as a flow path for discharging the cooling gas from 16 to the outside. Although not shown, the cylinder head 105 has
A suction port for supplying the cooling gas to the suction chamber 142 and a discharge port for sending the cooling gas from the discharge chamber 143 to the outside are provided.

Next, referring to FIGS. 2 to 4, the compressor 10 will be described.
The valve mechanism 1 will be described. As shown in FIG. 2, the compressor 101 has a through hole portion 112 of the cylinder block 104.
7 cylinders are provided with seven cylinders 116 around them, and the valve plate 106, the cylinder gasket 107, the intake valve member 129 and the discharge valve member 133 made of spring material, the discharge valve receiving member 135, etc. It has a shape corresponding to. That is, the suction valve member 129 and the discharge valve member 13
The discharge valve receiving member 3 and the discharge valve receiving member 135 are plate-like elastic members that are radially branched from the central portion in seven directions. Further, the valve plate 106 has seven suction holes 131 and seven discharge holes 132.

Each of the intake valve member 129, the valve plate 106, the discharge valve member 133, and the discharge valve receiving member 135 has
Screw holes 129a, 106a, 13 having the same diameter in the center
3a and 135a are drilled. Then, the members are stacked in this order, and the screws 145,
It is screwed by a washer 146 and a nut 147. At this time, the tip side of each suction valve of the suction valve member 129 closes each suction hole 131 of the valve plate 106, the tip side of each discharge valve of the discharge valve member 133 blocks each discharge hole 132 of the valve plate 106, and The discharge valve receiving member 135 is fixed by screws so as to be flush with the discharge valve member 133 in a plane. As a result, each of the substantially oval holes 148 formed in the intake valve member 129 on the proximal end side of each intake valve communicates with each discharge hole 132 of the valve plate 106.

As shown in FIG. 2, the cylinder block 10
Recesses 134 are formed at the upper ends of the four cylinders 116. Each recess 134 is a notch groove formed at a predetermined depth from a joint plane 151 which is a joint with the cylinder gasket 107, and has a substantially crescent-shaped plane. Each recess 134 is formed at a position on the upper end side of each cylinder 116 on an extension line of an imaginary line connecting the center of the circle formed by the through hole 112 and the center of the circle formed by the cylinder 116.

The cylinder gasket 107 is provided at its center with a hole 152 having the same planar shape as the through hole 112 of the cylinder block 104.
A cylinder hole 153 having the same plane shape as that of the cylinder 116 and the recess 134 and a screw hole 154 through which a screw penetrates are provided on the outer side of 2.

The head gasket 130 is provided with a hole 155 in the center thereof over a wide area, and the hole 155 is formed.
Seven suction hole portions 156 corresponding to the suction holes 131 of the valve plate 106 are provided on the outer side of the.

By assembling these members using a plurality of screws 157, as shown in FIG. 3, the tips 129b of the intake valves of the intake valve member 129 are arranged at the positions of the recesses 134 of the cylinder block 104, respectively. To be done. In FIG. 3, the center position of the cylinder 116 is indicated by the point P.

In the compressor 101 having such a structure, when the drive shaft 108 is rotated by a driving force from the outside such as an engine or a motor, the rotor 118 is integrally rotated, and the rotor 118 is rotated via the hinge mechanism. Plate boss 121
The rotational movement is transmitted to the swash plate boss 121, and the swash plate boss 121 rotates synchronously with the drive shaft 108 at a predetermined inclination angle. The swing plate 1 is connected to the swash plate boss 121 so as to be rotatable relative thereto.
The one end of the member 22 reciprocates along the guide member 128, so that the member 22 swings at a predetermined inclination angle without rotating in the crank chamber 117. At this time, in the compressor 101, the plurality of pistons 110 reciprocate in the cylinder 116, respectively, and the pistons 110 that have come to the position of the ear portion 124 of the rotating rotor 118 are sequentially pushed up to reach the top dead center. Become.

In the compressor 101, when the cooling gas from a gas-liquid separator, an evaporator (evaporator) or the like (not shown) is supplied to the suction chamber 142 in the cylinder head 105 and the piston 110 moves to the bottom dead center side, As shown in FIG. 4, the suction valve of the suction valve member 129 is elastically deformed to open to the cylinder 116 side to release the blockage of the suction hole 131 of the valve plate 106, and the cooling gas is sucked into the suction hole 131 of the valve plate 106. Is sucked into the cylinder 116 via the. At this time, the displacement amount of the suction valve due to the elastic deformation is limited by the recess 134. Specifically, as shown in FIG. 4, the distal end portion 129b thereof has a depth L _{1 of the} recess 134.
It is possible to displace by the amount.

When the piston 110 moves to the top dead center side, the cooling gas in the cylinder 116 is compressed, and the discharge valve of the discharge valve member 133 is elastically deformed by the compressed cooling gas so that the cylinder head 105 side. The cooling gas is discharged into the discharge chamber 143 through the discharge hole 132 of the valve plate 106. Then, the cooling gas is discharged from the discharge port of the cylinder head 105 to the outside and is supplied to a radiator or the like (not shown).

In the compressor 101, the engagement position of the long hole portion 125a in the ear portion 125 of the swash plate boss 121 with respect to the engagement pin 124a of the ear portion 124 on the rotor 118 side moves due to the load fluctuation of the cooling gas. As a result, the inclination angle of the swash plate boss 121 changes, so that the cylinder 11
The capacity of the refrigerant gas that can be sucked into 6 changes.

[0026]

By the way, in such a variable displacement type compressor 101, the tip portion 129b of the intake valve abuts on the recess 134 at the time of low load operation or the like in which the amount of gas passing therethrough becomes small. However, the natural vibration of the intake valve causes the intake valve to vibrate, causing pressure pulsation, which causes unpleasant noise in the vehicle.

The state of this noise is shown by (2) in FIG.
The inhaled gas causes the tip portion 129b of the intake valve and the recess 13
4 flows through between the narrow tip 129b and the recess 129b along the recess 134 for nearly 180 °, causing peeling to form a vortex, and the vortex and the natural frequency of the valve match. If so, a resonance phenomenon occurs, which causes pressure pulsation and noise.

As a method of coping with such a problem, it is conceivable to make the depth L ₁ of the recess 134 in the cylinder 116 shallow, but in this case, when the amount of gas passing through becomes large, A sufficient amount of gas cannot be sucked into 116, and the desired performance cannot be obtained.

As a conventional configuration example for preventing the valve vibration of the suction valve, for example, the techniques described in JP-B-53-16012 and JP-B-53-32881 are known. In each of these publications, a valve plate (cylinder head plate 11) corresponding to the center position of the cylinder (position of point P in FIG. 3) is disclosed.
There is described a configuration in which a stopper for limiting the movable range of the intake valve is provided at the relevant portion, and a concave portion for receiving this stopper is formed at the center of the piston (14).

However, in the case of such a structure, the concave portion at the center of the piston becomes a dead space, and there arises a problem that the volume efficiency is lowered. Also, the actual public 5
In the configuration described in Japanese Patent Laid-Open No. 3-32881, the displacement of the valve tip portion is not regulated. Therefore, in the case of liquid compression, the suction valve may be extremely deformed and damaged.

The present invention has been proposed in view of the above circumstances, and provides a reciprocating compressor having a suction valve mechanism capable of preventing noise due to vibration of the suction valve at a low load. The purpose is to do.

[0032]

In order to solve the above problems, the present invention provides a cylinder block having a cylinder in which a piston reciprocates, and a suction hole and a discharge hole for sucking and discharging a refrigerant by the reciprocating movement of the piston. A valve plate attached to the top of the cylinder of the cylinder block, and an intake valve made of an elastic member attached to the valve plate so as to close the intake hole. When the intake valve is elastically deformed in the opening direction of the intake hole, the tip of the intake valve comes into contact with the valve receiving part that is cut out at a predetermined depth from the top of the cylinder, so that the lift amount of the intake valve increases. In a regulated reciprocating compressor, the suction valve has a vortex reduction portion for preventing vibration of the valve formed in a valve receiving portion with which a valve tip portion of the suction valve abuts. Is the tip of the suction valve and the The flow is concentrated near the axis 0-0 by providing the cross section of the valve receiving part on the lower end side of the intake valve with an R shape or a non-R shape so that the flow entering from the intake port to the part where the Like this,
(EN) Provided is a reciprocating compressor in which vortex flow is reduced to prevent vibration of a suction valve at a low load, and pressure pulsation and noise are removed as much as possible.

The feature of the present invention is that the vortex of the flow entering from the suction port at the portion where the tip of the suction valve and the valve receiving portion come into contact is reduced, and the sectional shape of the valve receiving portion on the lower end side of the suction valve is reduced. Is formed as an R shape or a non-R shape so as to have a groove shape with respect to the suction direction of the axis 0-0 direction drawn substantially in the center of the intake valve main body, and the flow gathers near the axis 0-0. It was done like this.

[0034]

[0035]

[0036]

[0037]

In the reciprocating compressor of the present invention, when the flow rate of the gas to be sucked is small, the suction valve is not in contact with the valve receiving portion of the cylinder block, but the vortex reduction portion of the valve receiving portion prevents the lower surface of the valve. Flow that forms a vortex along is prevented and valve oscillation is avoided. Then, when the gas flow rate increases, the displacement of the intake valve is regulated as a whole by the front end of the intake valve body contacting the valve receiving portion of the cylinder block.

[0039]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. The reciprocating compressor of the present invention is shown in FIGS.
It can be suitably applied to the conventional compressor 101 described in FIG. 4, and in each embodiment described below, the intake valve mechanism, that is, the configuration of the intake valve and the cylinder block side that receives the movement of the intake valve is , Each is different from the conventional one. Hereinafter, in order to avoid redundancy, the description of the entire compressor is omitted as appropriate, and FIGS. 1 to 4 are cited as necessary.

The first embodiment of the reciprocating compressor of the present invention will be described with reference to FIG. The intake valve mechanism 10 shown in FIG. 5, as described in FIG.
The cylinder body 1 of the cylinder block 12 includes a valve body portion 13, a hole portion 15, a valve tip portion 16, and a valve receiving portion 18 that limits displacement of the valve.
Prepared within 7.

As described with reference to FIG. 2, the intake valve member 11 has a valve body portion 13 corresponding to the number of pistons and cylinders.
Is branched, and in this example, seven valve body portions 13 are formed from the center. Each of the valve main body portions 13 has a substantially oval hole portion 15 formed on the base end side thereof. The hole 15 is formed in the same shape and at the same position as the hole 148 shown in FIG. The valve tip 16 of the valve body 13 has a tapered shape, which is also the same as the tip 129b shown in FIG.

As shown in FIG. 3, the intake valve member 11 has its valve tip portion 16 brought into contact with a valve receiving portion 18 which is a notch groove provided in the cylinder 17.

On the other hand, the cylinder block 12 is different from the cylinder block 104 described in FIGS. 1 to 4 in the shape of the valve receiving portion 18. Cylinder block 12
7, seven cylinders 17 having the same diameter as the cylinder 116 are formed, and a valve receiving portion (recess) 18 is formed in each cylinder 17 at a predetermined depth (L ₁ ) from the above-mentioned joining plane 151. The recess 18 is formed in the same shape and at the same position as the recess 134 shown in FIGS.

In FIG. 6, the valve receiving portion 18 is provided with the eddy current reducing portion 19 at the corner 18a of the valve receiving portion 18.
The cross section has an R shape, and the flow entering from the suction port 131 flows through a smooth portion of the R shape even at the time of low load operation. It is prevented from flowing along to generate a vortex.
In the present invention, the R-shaped portion 19 that prevents the flow from flowing from the direction of the valve tip portion 16 along the lower surface of the valve to generate a vortex is eliminated by eliminating the right angled corner portion as described above.
The pulsation and vibration due to the vortex will not occur.

According to the reciprocating compressor having the suction valve mechanism 10 as described above, the cooling gas from the gas-liquid separator, the evaporator (evaporator) or the like (not shown) is supplied to the suction chamber 142 in the cylinder head 105. When the piston 110 moves to the bottom dead center side, the valve body portion 13 of the suction valve member 11 elastically deforms and opens toward the cylinder 17 side to release the blockage of the suction hole 131 of the valve plate 106, and the cooling gas is discharged. It is sucked into the cylinder 17 through the suction hole 131.

At this time, in the suction valve mechanism 10, when the flow rate of gas to be sucked increases, the valve tip portion 16 of the valve body portion 13 comes into contact with the recess 18 to restrict the displacement. Become.

Therefore, according to such an intake valve mechanism 10, during low load operation or the like in which the amount of passing gas is reduced,
Even when the valve tip 16 of the valve body 13 does not come into contact with the recess 18, no vortex flow is generated from the valve tip 16, so that vibration of the intake valve due to natural vibration does not occur and pressure pulsation causes discomfort. It is possible to prevent unnecessary noise.

In FIG. 7, the shape of the valve receiving portion 18 will be described in more detail. The valve receiving portion 18 has a cross-sectional shape of the valve receiving portion 18 on the lower end side of the intake valve member 11 which is R so that the flow entering from the suction port at the portion where the tip of the intake valve member 11 and the valve receiving portion 18 come into contact reduces the vortex. The shape of the R-shaped R is large and small as the cross-sectional shape of each of the valve receiving portions increases in the direction perpendicular to the axis 0-0 drawn substantially in the center of the intake valve body. The flow is concentrated near the axis 0-0. 7 (2) shows the cross-sectional shape of the valve receiving portion 18 at point A, and FIG. 7 (3) shows the cross-sectional shape at point B. The relationship between the radius of the R-shaped cross section and the point B distant from the axis is R
_A > R _B.

Regarding the shape of the valve receiving portion 18 seen from the plane, as shown in (4) of FIG. 7 from the point A to the point B ((4) of FIG. 7 is the axis 0-0. Although a cutaway perspective view of the valve receiving portion 18 is shown), it is also possible to form an eddy current reducing portion 190 in which the corners from the central corner 18a to the end 18b have an R shape and the R diameter is gradually reduced in a curved shape. It is more preferable that the flow is not suddenly changed, the eddy current is not further generated, and further reduced. With such a shape, the axis 0
Since the flow gathers near −0, a matched flow is formed, the pressure drops, and the valve tip 16 is pulled by the valve receiving portion 18, so that vibration does not occur. Furthermore, if the corner portion 18b of the wall of the cylinder 17 of the valve receiving portion 18 also has an r shape, the flow becomes smoother, the vortex flow is reduced, and the vibration of the valve is reduced.

A second embodiment of the reciprocating compressor of the present invention will be described with reference to FIG. In the embodiment shown in FIGS. 6 and 7, the cross-sectional shape of the eddy current reducing portion 19 of the valve receiving portion 18 is
Although it was R-shaped, various other shapes can be considered as the shape for preventing eddy currents.

The shape of the eddy current reducing portion 19 shown in FIG. 8 is different from that of the R shape shown in FIGS. As another modification of the shape of the eddy current reducing portion 19, the one shown in FIG.
The cross-sectional shape of the eddy current reducing portion 19 is not R-shaped but non-R-shaped,
An example is a straight line that is cut diagonally.

As shown in FIG. 8B, the eddy current reducing portion 19 is formed into a slanted portion 19 by separating the corner portion 18a into a slanting linear shape.
It can also be formed as 1 and so-called chamfered to change the flow direction and reduce the vortex. In this case, the production is very easy because it is simply cut out.

An alternative embodiment of the reciprocating compressor of the present invention will be described with reference to FIG. The embodiment of FIG. 9 has a shape obtained by inclining and cutting with a linear plane as in the case of FIG. This modification shows an intermediate form between FIG. 7 and FIG. 8, but as seen in the cross section of the drawing, it is substantially symmetrical with respect to the axis 0-0 direction drawn in the approximate center of the intake valve main body. And the groove is inclined toward the suction direction so that the flow is 0-0.
It was designed to gather near.

A third embodiment of the reciprocating compressor of the present invention will be described with reference to FIG. In the example shown in FIG. 9, the cross-sectional shape of the vortex flow reducing portion 19 of the valve receiving portion 18 does not have an R shape, but is formed by inclining and cutting with a linear plane as in FIG. This modification is shown in FIG.
As shown in the cross section of the figure, the corner portion 180 is cut into a slanting slope shape, so-called corner cutting is performed, and the cut volume is gradually reduced as the distance from the axis 0-0 is increased. Since the slanted inclined portion 193 is formed,
It can be seen that a flow conforming to (4) in (4) can be formed. Also,
There is an advantage that it can be easily formed because it can be cut out in an obliquely inclined shape in manufacturing.

According to the reciprocating compressor having the suction valve mechanism 10 having the second and third embodiments, the cooling gas is supplied to the suction chamber 14 in the cylinder head 105 as described above.
2 and the piston 110 moves to the bottom dead center side, the valve body 13 of the suction valve member 10 elastically deforms and opens to the cylinder 17 side, releasing the blockage of the suction hole 131 of the valve plate 106, The cooling gas is sucked into the cylinder 17 through the suction hole 131. At this time, in the intake valve mechanism 10, the valve tip 16 contacts the cylinder 17a, and the shape from the center of the valve body 13 to the valve tip 16 changes.

Therefore, according to the intake valve mechanism 10 as described above, even if the valve tip 16 of the valve body 13 does not contact the valve receiving portion 18, vortex flow does not occur, so that valve vibration is suppressed. Act as you do. That is, according to the reciprocating compressor including the suction valve mechanism 10, when the valve tip portion 16 of the valve body portion 13 does not come into contact with the valve receiving portion 18 at the time of low load operation or the like in which the amount of passing gas decreases. Even in this case, the self-excited vibration of the suction valve does not occur, and it is possible to prevent unpleasant noise due to pressure pulsation.

Particularly, if the width h of the eddy current reducing portions 191, 192, 193 is set as d> h from the tip end width d of the suction valve, the flow is generated from the lower end of the valve tip end portion 16 and the speed is increased. According to Bernoulli's theorem, the valve tip 16
A pressure drop occurs below, and as a result, the valve tip portion 16 is sucked against the bottom surface of the valve receiving portion 18, and the valve receiving portion 18
Can be more easily attached to the bottom surface, and the vibration of the valve can be more effectively prevented. Of course, even if d <h is set, the flow will flow from the side of the valve tip 16 to the lower side of the valve tip 16, causing a pressure drop and sucking the valve.

In the embodiment shown in FIGS. 8 and 9 as well,
As described with reference to FIG. 7, it is needless to say that the r-shaped portion may be provided in the corner portion 18b for reducing the eddy current, as shown in (1) of FIG. 10 when the FIG. 9 is viewed from the XX direction. . Of course, the corner portion 18b may be formed in an oblique shape having a simple structure instead of the r shape (see (2) in FIG. 10).

If the flow at the corner portion 18b is a right angle, a vortex flow is generated at the corner portion 18b and the valve tip portion 16 at the corner portion 18b as shown in (3) of FIG. Can be. However, if it is formed as an r shape or an oblique shape, the energy of the vortex is reduced as shown in (4) of FIG. 10, and a large vortex is not generated, so that the influence or action on the valve tip 16 can be removed. As a result, the flow from the corner portion 18b to the valve tip portion 16 and the valve receiving portion 18 goes straight, so that the effect of further reducing the eddy current becomes preferable. Any of these corners 18b can be utilized as an auxiliary for reducing eddy currents, and various eddy current reducing units 19 can be combined with those skilled in the art.

In each of the above-described embodiments, the case where the present invention is applied to a so-called 7-cylinder reciprocating compressor having seven pistons and cylinders has been described, but the present invention is not limited to this. 5 cylinders, 6 cylinders,
It can be applied to reciprocating compressors having various numbers of cylinders.

[0061]

As described in detail above, according to the reciprocating compressor of the present invention, when the suction valve is elastically deformed in the opening direction of the suction hole due to the movement of the piston in the direction of the bottom dead center, the suction valve is sucked. When the flow rate of the generated gas is small, even if the reed piece is not in contact with the reed piece receiving portion formed on the cylinder block, the eddy current reducing portion prevents the valve vibration. Therefore,
According to the present invention, it is possible to provide a reciprocating compressor that can prevent noise due to vibration of the suction valve when the load is low.

Further, according to the reciprocating compressor of the present invention,
With a very simple structure, it is possible to prevent noise due to the pulsation of the intake valve at the time of low load by cutting without adding any special member.

Further, since the vortex flow is reduced and the valve tip end portion is actuated so as to be attracted to the valve receiving portion, the vibration of the valve can be further stabilized and a preferable vibration preventing effect can be obtained. .

Further, the shape and structure of the eddy current reducing portion makes it possible to reduce the eddy current and obtain a reciprocating compressor with stable performance in which pressure pulsation and noise are removed as much as possible.

[Brief description of drawings]

FIG. 1 is a cross-sectional view illustrating an entire configuration of an example of a conventional reciprocating compressor.

FIG. 2 is an exploded perspective view showing a configuration example of a valve mechanism in the reciprocating compressor.

FIG. 3 is a plan view showing a positional relationship between a suction valve and a cylinder in the reciprocating compressor.

FIG. 4 is a cross-sectional view for explaining the operation of the suction valve.

FIG. 5 shows an intake valve according to an embodiment of the present invention.

FIG. 6 shows a state in which a suction valve of the reciprocating compressor of the present invention flows into the valve from the suction valve in the first embodiment.

FIG. 7 shows the R of the valve receiving portion in the first embodiment.
The example of the shape of a shape part is shown.

FIG. 8 is a second part of the reciprocating compressor of the present invention, such as a suction valve.
An embodiment of is shown.

FIG. 9 is a perspective view of a valve receiving portion in the third embodiment of the suction valve and the like of the reciprocating compressor of the present invention.

FIG. 10 shows the X- of FIG. 9 in the third embodiment.
The cross-sectional view of the valve-receiving part seen from the X direction, and the flow condition are shown.

[Explanation of symbols]

10 Intake valve mechanism 11 Intake valve member 12 cylinder block 13 Valve body 15 Hole with a substantially oval shape 16 valve tip 17 cylinders 151 joining plane 18 Valve receiving part (recess) 18a, 18b corners 19 Eddy current reduction unit 190-192 Eddy current reduction unit

─────────────────────────────────────────────────── --- Continuation of the front page (56) References JP-A-6-272667 (JP, A) JP-A-2000-274367 (JP, A) Actually opened 54-149720 (JP, U) Actually opened 56-84168 (JP, U) Actual Kai 4-1682 (JP, U) Actual public 55-26618 (JP, Y1) Actual public 53-16012 (JP, Y1) Actual public 53-32881 (JP, Y1) (JP, Y1) 58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 39/10

Claims (3)

(57) [Claims] 1. A cylinder block having a cylinder in which a piston reciprocates, and a suction hole and a discharge hole for sucking and discharging a refrigerant by the reciprocating movement of the piston,
A valve plate mounted on the top of the cylinder of the cylinder block and a suction valve made of an elastic member mounted on the valve plate so as to close the suction hole are provided. When the suction valve elastically deforms in the opening direction of the suction hole, the tip of the suction valve comes into contact with the valve receiving portion that is formed by notching at a predetermined depth from the top of the cylinder. In the reciprocating compressor in which the lift amount of the suction valve is regulated, the suction valve has a vortex flow reducing portion for preventing vibration of the valve in the valve receiving portion with which the valve tip portion of the suction valve abuts, The eddy current reducing portion has a groove-shaped cross section of the valve receiving portion on the lower end side of the intake valve so that the flow entering from the intake port at the portion where the tip of the intake valve and the valve receiving portion contact each other reduces the eddy current. Provided, the cross-sectional shape of the valve receiving portion is a suction valve It is characterized in that the diameter of R of the above-mentioned R shape is changed from large to small as it goes in a direction perpendicular to the axis 0-0 drawn in the approximate center of the body, so that the flow gathers near the axis 0-0. A reciprocating compressor. 2. A cylinder block having a cylinder in which a piston moves reciprocally, and a suction hole and a discharge hole for sucking and discharging refrigerant by the reciprocating movement of the piston,
A valve plate mounted on the top of the cylinder of the cylinder block and a suction valve made of an elastic member mounted on the valve plate so as to close the suction hole are provided. When the suction valve elastically deforms in the opening direction of the suction hole, the tip of the suction valve comes into contact with the valve receiving portion that is formed by notching at a predetermined depth from the top of the cylinder. In the reciprocating compressor in which the lift amount of the suction valve is regulated, the suction valve has a vortex flow reducing portion for preventing vibration of the valve in the valve receiving portion with which the valve tip portion of the suction valve abuts, The vortex reduction section is provided with a non-R-shaped cross-sectional shape of the valve receiving section on the lower end side of the suction valve so that the flow entering from the suction port at the portion where the suction valve tip and the valve receiving section come into contact reduces the vortex flow. The R shape is the axis 0 drawn in the approximate center of the intake valve body. The lower end side of the intake valve was slanted with respect to the suction direction of 0 direction, and the circumferential direction was slanted toward the axis 0-0 to form a groove, so that the flow gathered near the axis 0-0. A reciprocating compressor characterized in that 3. A cylinder block having a cylinder in which a piston reciprocates, and a suction hole and a discharge hole for sucking and discharging a refrigerant by the reciprocating movement of the piston,
A valve plate mounted on the top of the cylinder of the cylinder block and a suction valve made of an elastic member mounted on the valve plate so as to close the suction hole are provided. When the suction valve elastically deforms in the opening direction of the suction hole, the tip of the suction valve comes into contact with the valve receiving portion that is formed by notching at a predetermined depth from the top of the cylinder. In the reciprocating compressor in which the lift amount of the suction valve is regulated, the suction valve has a vortex flow reducing portion for preventing vibration of the valve in the valve receiving portion with which the valve tip portion of the suction valve abuts, The vortex reduction section is provided with a non-R-shaped cross-sectional shape of the valve receiving section on the lower end side of the suction valve so that the flow entering from the suction port at the portion where the suction valve tip and the valve receiving section come into contact reduces the vortex flow. The R shape is the axis 0 drawn in the approximate center of the intake valve body. By arranging the grooves so that they are inclined symmetrically with respect to the 0 direction and diagonally inclined toward the suction direction, the flow will be
A reciprocating compressor characterized by gathering near 0.