JP2002061577A - Reciprocating compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid abrupt pressure rise in a cylinder in a reciprocating compressor during compressing a gaseous refrigerant. SOLUTION: The opening of a discharge port 92 on the side of insertion of the head of a rivet 110 is chamfered to form an auxiliary passage for escaping the pressure of the gaseous refrigerant. Otherwise, a groove 162 can be provided in a rivet 160.

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 a reciprocating compressor suitably used as a component of an air conditioner for an automobile.

[0002]

2. Description of the Related Art An air conditioner for a vehicle usually includes a condenser, an evaporator, a compressor and the like. The air introduced from the outside is sent to the evaporator and exchanges heat with the liquid refrigerant flowing through the tubes of the evaporator. As a result, the air is cooled by depriving the latent heat, and the cooled air is used for cooling the interior of the vehicle. On the other hand, the liquid refrigerant evaporates to a gaseous refrigerant.

[0003] The liquid refrigerant is then heated to a high temperature by a compressor.
High pressure is applied. Thereafter, the air is sent to a condenser, and is condensed by being cooled in the condenser to become a gaseous refrigerant. When the gaseous refrigerant is brought into a high-temperature and high-pressure state by the compressor, the condensation of the gaseous refrigerant in the condenser becomes relatively easy. Then, after the liquid refrigerant is sent to the evaporator, the above-described cycle is repeated to continuously cool the interior of the vehicle.

[0004] A reciprocating compressor is exemplified as a compressor having the above-mentioned operation.
2. Description of the Related Art A so-called swash plate type compressor in which a piston fitted to a swash plate reciprocates in a cylinder as the swash plate rotates is widely used.

[0005] As one type of such a swash plate compressor, a gaseous refrigerant fed from an evaporator and introduced into a cylinder is sent to a compression chamber of the cylinder through an intake port provided in a piston. It has been known. In this case, the outlet of the intake port is provided on one side wall surface in the lateral direction of the piston, and an intake valve covering the intake port is connected to the one side wall surface by a fixing member. The suction valve opens when the pressure of the gaseous refrigerant that has reached the inside of the intake port becomes equal to or higher than a predetermined value. Thereby, the gaseous refrigerant introduced into the compression chamber of the cylinder is compressed under the action of the piston.

When the pressure of the gaseous refrigerant becomes equal to or higher than a predetermined value due to the compression, the discharge valve opens, and as a result, the compressed gaseous refrigerant is discharged from the cylinder. The gaseous refrigerant is sent to the condenser via the outlet port of the compressor.

[0007]

In the swash plate compressor of this type, when the gaseous refrigerant is compressed by the piston, the head of a rivet or screw connecting the suction valve to the piston is inserted into the discharge port. (See, for example, JP-A-55-46063). In this case, since the dead point of the piston can be made closer to the discharge port side, a large amount of the compressed gaseous refrigerant can be led out of the cylinder, and as a result, the compression efficiency of the gaseous refrigerant is improved. It is.

However, if the discharge port is formed in the same shape and penetrates from the side where the head of the rivet or screw is inserted, immediately before the piston reaches the dead center, that is, the head of the rivet or screw is discharged. Immediately before being inserted into the outlet, there is a problem that the passage of the gaseous refrigerant is significantly restricted by the discharge port and the head approaching the discharge port.

[0009] Under such circumstances, the pressure of the gaseous refrigerant in the cylinder rises temporarily but significantly. For this reason, an extremely large load acts on the piston, the suction valve, and the like, and there is a concern that these members may be damaged.

[0010] In particular, immediately after the operation of the compressor is started, the liquid refrigerant may flow into the cylinder, and in this case, the pressure in the cylinder during compression increases.

When the pressure in the cylinder increases,
Inevitably, the work of the power source for energizing the compressor increases.
For this reason, for example, in the case of an air conditioner for a vehicle, since a power source is an internal combustion engine for a vehicle, a problem that fuel efficiency is reduced is caused.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problem, and it is possible to avoid an increase in the pressure in a cylinder when compressing a gaseous refrigerant. It is an object of the present invention to provide a reciprocating compressor capable of avoiding damage to the compressor and an increase in the work of the power source.

[0013]

According to the present invention, there is provided a reciprocating compressor for compressing a fluid by reciprocating a piston in a cylinder, the piston having a suction port. A suction valve that can open and close the suction port, a fixing member that connects the suction valve to the piston, and a discharge port into which the fixing member is inserted when the piston reaches a dead center in the cylinder. And an auxiliary passage for releasing pressure of gas compressed by the piston is provided in at least one of the discharge port and the fixed member.

With such a configuration, when a fluid such as a gaseous refrigerant is compressed by the piston, the pressure of the gas can be released through the auxiliary passage. That is, it is possible to avoid a sudden increase in the pressure in the cylinder, thereby avoiding damage to the piston, the suction valve, and the like.

Preferred examples of the fixing member include rivets and screws.

The auxiliary passage can be formed, for example, by providing a chamfer on the inlet side of the fixing member at the discharge port. Alternatively, the fixing member may be formed by providing a chamfer or a groove.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of a reciprocating compressor according to the present invention will be described below in detail with reference to the accompanying drawings.

FIG. 1 is a schematic cross-sectional view of a reciprocating compressor according to the present embodiment. In the reciprocating compressor 10, the piston 16 fitted to the swash plate 14 rotates with the rotation of the swash plate 14 fixed to the rotating shaft 12 in a state of being inclined at a predetermined angle. It reciprocates in the cylinder 18. That is, the reciprocating compressor 10 is a so-called swash plate compressor, and is suitably used in an air conditioner for an automobile to send gaseous refrigerant from an evaporator to a condenser.

The casing of the reciprocating compressor 10 includes:
Rear housing 20, rear cylinder block 22, front cylinder block 24 and front housing 2
6 are connected in this order from the left, and valve plates 28 and 28 are interposed between the rear housing 20 and the rear cylinder block 22 and between the front cylinder block 24 and the front housing 26, respectively. I have. The two valve plates 28, 28, the rear cylinder block 22, and the front cylinder block 2
4, five cylinders 18 separated from each other at an angle of 72 ° are formed inside the casing as shown in FIG. 2 which is a schematic sectional view taken along line II-II in FIG. Of course, the pistons 16 are arranged in all the cylinders 18.

At the center of one end of the front housing 26 (see FIG. 1), a hollow cylindrical portion 30 is formed so as to protrude therefrom.
An electromagnetic clutch 32 is rotatably fitted to the outer peripheral wall of the hollow cylindrical portion 30 via a bearing 33. Further, an introduction port 34 and an outlet port 36 are formed in the rear cylinder block 22, and a chamber 40 communicating with the outlet port 36 via a flow path 38 is formed in the rear cylinder block 22 and the front cylinder block 24. Have been.

On the other hand, the rear cylinder block 22, the front cylinder block 24 and the front housing 26
Are formed with through holes 42, 44 and 46, respectively, and the rotating shaft 12 is accommodated in the casing by passing through the through holes 42, 44 and 46. Radial bearings 48 are interposed between the rotary shaft 12 and the through holes 42, 44 of the rear cylinder block 22 and the front cylinder block 24, respectively.
The rotating shaft 12 is rotatably supported by the rear cylinder block 22 and the front cylinder block 24 via the radial bearings 48, 48. A seal is provided between the through hole 46 of the front housing 26 and the rotating shaft 12 by a seal member 50.

The through hole 46 of the front housing 26
It communicates with the hollow portion of the hollow cylindrical portion 30 through a small through hole 52 having a smaller diameter than the through hole 46. One end of the rotating shaft 12 is supported by the front housing 26 by projecting through the small through hole 52 to the outside of the hollow cylindrical portion 30. A bolt hole 54 is formed at one end of the protruding rotary shaft 12, and the rotary shaft 12 and a hub 58 constituting the electromagnetic clutch 32 are connected to each other by a bolt 56 screwed into the bolt hole 54. I have.

First to fourth discs 60, 62, 64, 66 are fitted in the center of the rotating shaft 12, and
A first thrust bearing 68 is provided between the disk 60 and the second disk 62, and the second disk 62 and the third disk 6
4, a swash plate 14 is provided between the third disk 64 and the fourth disk 66, and a second thrust bearing 70 is provided between the swash plate 14 and the fourth disk 66.

The disk portion of the swash plate 14 extends into the cylinder 18 formed by the rear cylinder block 22, the front cylinder block 24 and the two valve plates 28. The piston 16 is fitted to the disc via hemispherical shoes 72, 72. As will be described later, the piston 16 reciprocates in the cylinder 18 as the swash plate 14 rotates. I do.

The piston 16 is, as shown in FIG.
It is almost symmetrical. The piston 16 includes first and second disk portions 74a and 74b, and the first and second disk portions 7a and 74b.
4a, 74b, first and second suction portions 80a, 80b having taper portions 76, 76 tapered in diameter and shoe receiving portions 78, 78 formed with hemispherical grooves 77, 77, respectively. The shoe receiving portions 78 are integrally formed with a connecting portion 82 connecting the shoe receiving portions 78 to each other. In addition, the first intake unit 80a and the second intake unit 80b are connected to the shoe receiving unit 7.
8 and 78 are arranged so as to face each other and to be separated by a predetermined interval.

The maximum height of the connecting portion 82 is set to be slightly lower than the center of the hemispherical groove 77 of each shoe receiving portion 78 in FIG. 3 in order to secure the escape of the swash plate 14.

As shown in FIG. 4, a web portion 84 protrudes from the connecting portion 82 in parallel with the diameter direction of the first and second disk portions 74a and 74b.
Is bridged from the first disk part 74a to the second disk part 74b. That is, the first and second disk portions 74
The a and 74b are integrally connected to each other via a web portion 84, whereby the rigidity of the connecting portion 82 is improved.

The height of the web portion 84 is set to the same height as the connecting portion 82 (see FIG. 3). When the web portion 84 is made higher than the connecting portion 82, the shoe receiving portion 78 of the web portion 84
This is because post-processing such as notching a portion between the 78s is necessary.

Grooves 86, 86 are provided in the side peripheral wall portions of the first and second disk portions 74a, 74b, respectively (see FIG. 3), and the ring-shaped seal member 8 is provided in the grooves 86, 86.
8, 88 are fitted. First and second disk portions 74
The thickness of the ring-shaped sealing members 88, 8
It is slightly larger than 8.

The first and second disk portions 74a, 74b are
It is supported by the tapered portions 76, 76. In this case, the weight of the piston 16 can be reduced as compared with the case where the thicknesses of the first and second disk portions 74a and 74b are large. The first and second disk portions 74 are located above the tapered portions 76 of the first and second intake portions 80a and 80b.
A bent portion 90 is provided by being bent at an obtuse angle while the diameter is reduced from a, 74b toward the shoe receiving portions 78, 78.

That is, the piston 16 is reduced in weight by the first and second disk portions 74a, 74b being supported by the tapered portions 76, 76 and the web portion 84 (see FIG. 4) being provided. Rigidity has been improved.

As shown in FIG. 5, which is a front view of the piston 16, the first and second disk portions 74a and 74b are moved from the first and second intake portions 80a and 80b to the tapered portions 76 and 7b.
6 until the gaseous refrigerant introduced from the introduction port 34 of the casing (see FIG. 1) reaches the valve plate 2.
Three intake ports 94a to 94c for supplying air to the discharge ports 92, 92 formed in the holes 8, 28 are formed to penetrate therethrough. Openings of the intake ports 94a to 94c on the first and second disk portions 74a and 74b side are respectively provided with openable and closable intake valves 9.
8, 98 are arranged.

As shown in FIG. 6, the suction valve 98 has an opening / closing portion 100 for opening and closing the intake ports 94a to 94c, and first and second disk portions 7 extending from both ends of the opening / closing portion 100.
First and second loop-shaped arm portions 102a and 102b curved along the outer periphery of the first and second loop-shaped arms 4a and 74b;
A connecting portion 104 which rises vertically from a connecting portion between the loop-shaped arm portions 102a and 102b, and a fixing portion 1 which is disposed at a distal end portion of the connecting portion 104 and provided with a U-shaped hole 106;
08, and a rivet hole 11 in which a rivet 110 (see FIGS. 1, 3, 4, and 5) as a fixing member having a body portion passed through the U-shaped hole 106 is provided in the piston 16.
2 (see FIGS. 1 and 3)
And the second disk portions 74a and 74b. The suction valve 98 is constantly pressed toward the first and second disk portions 74a and 74b by the head of the rivet 110, and thereby the rotation of the suction valve 98 is prevented.

Here, as shown in FIG. 7, a stopper 114 is formed on the side peripheral wall of the head of the rivet 110 so as to protrude. The corner of the end face of the stopper 114 on the side where the opening / closing section 100 comes into contact is curved.

As can be understood from FIG. 5, the rivet 110 is provided with a stopper portion 114 for opening and closing the opening / closing portion 100 of the suction valve 98.
Is fitted in the rivet hole 112 so as to face the rivet hole 112.
When the opening / closing section 100 is opened, the opening / closing section 100 contacts the stopper section 114 as described later.

Hemispherical grooves 77, 77 of the shoe receiving portions 78, 78 of the first and second intake portions 80a, 80b (see FIG. 3).
Accommodates hemispherical portions of hemispherical shoes 72, 72, and the flat portions of the hemispherical shoes 72, 72
(See FIG. 1) via the first and second disk portions 74a and 74b. That is, the swash plate 14 is sandwiched between two hemispherical shoes 72, 72, whereby the piston 16 is fitted to the swash plate 14.

As described above, the two valve plates 28 are formed with the discharge ports 92 for discharging the gaseous refrigerant compressed in the cylinder 18, respectively. Each of the cylinders 18 and each of the chambers 40 of the front housing 26 and the rear housing 20 are connected to these discharge ports 92,
92.

As shown in FIG. 8, each discharge port 92
It is tapered and reduced from the cylinder 18 toward the chamber 40. That is, the rivet 110 is
The opening on the side where is inserted is chamfered.

The shape of the discharge port 92 is the same as that of the cylinder 18.
On either the side or the chamber 40 side, the rivet 110 has a similar shape to the head, and is formed slightly larger than the head. That is, when the piston 16 reaches the dead center, as shown in FIG. 9, the head of the rivet 110 is inserted into the discharge port 92 with play.

The opening of the discharge port 92 on the chamber 40 side is
As shown in the figure, a discharge valve 116 is arranged. The discharge valve 116 includes an annular portion 118 and five branch portions 1 extending from the annular portion 118 and separated from each other by 72 °.
20 and a circular portion 12 formed at the tip of each branch portion 120.
2 are integrated. A large through-hole 124 is formed at the center of the annular portion 118, and the large through-hole 124 in the discharge valve 116 on the front housing 26 side has a rotating shaft 1.
2 is passed. Further, a pin hole 126 for passing a pin 125 (see FIG. 1) is provided around the large through hole 124. On the other hand, each circular portion 122 is
Is opened and closed freely.

As shown in FIG. 11, a discharge valve valve stopper 128 is arranged outside the discharge valve 116. The valve stopper 128 for the discharge valve is provided with the small annular portion 13.
0 and 7 extending from the small annular portion 130 to each other.
The branch part 120 of the discharge valve 116 (see FIG. 10) is integrally provided with five branch parts 132 separated by 2 °, and the branch parts 120 of the valve plates 28 and 28 and the valve stopper 128 for the discharge valve.
32. The branch portion 132 is bent toward the chamber 40 of the front housing 26 or the rear housing 20 from a position corresponding to the boundary between the branch portion 120 of the discharge valve 116 and the circular portion 122, and
(See FIGS. 1 and 11). As will be described later, when the circular portion 122 of the discharge valve 116 floats from the valve plates 28, the circular portion 122 is supported by being in contact with the bent portion 134 of the discharge valve valve stopper 128. With this support, the deformation of the discharge valve 116 is avoided.

The branch portions 132 of the discharge valve valve stopper 128 are connected to the large annular portion 13 integrated with the branch portions 132.
6 are connected to each other (see FIG. 11). A plurality of fixing portions 138 provided with bolt holes 137 are formed protruding from the large annular portion 136. That is,
Front cylinder block 24 and front housing 2
6 or between the rear cylinder block 22 and the rear housing 20.
28 is a front housing 2 through a bolt hole 137.
It is positioned and fixed to the casing by bolts (not shown) that connect from 6 to the rear housing 20.

Further, a pin hole 140 is provided in the small annular portion 130 of the discharge valve valve stopper 128 at a position corresponding to the pin hole 126 of the annular portion 118 of the discharge valve 116. The pin 12 passing through both the pin holes 126 and 140
5 (see FIG. 1) is the front cylinder block 24 and the front housing 26, or the rear cylinder block 22
And the rear housing 20, the discharge valve 116 is positioned and fixed to the casing.

Each chamber 40 of the rear housing 20 and each chamber 40 of the front housing 26 communicate with a flow path 38, and the flow path 38 communicates with an outlet port 36.
That is, each chamber 40 is connected to the outlet port 36 through the flow path 38.
To the reciprocating compressor 1 from the introduction port 34.
The gaseous refrigerant introduced into the cylinder 0 is compressed by the piston 16 in the cylinder, and then is discharged from the discharge port 36 through the discharge port 92 and the chamber 40.

The hollow cylindrical portion 30 of the front housing 26
Electromagnetic clutch 32 (see FIG. 1) fitted to the outer peripheral wall portion
Is a device for rotating or stopping the rotation of the rotating shaft 12.

The electromagnetic clutch 32 is connected to the hub 5 described above.
8, an annular clutch plate 142 connected to the hub 58 via a bolt 141, a rotor 144, and an electromagnet coil 146 housed in the rotor 144. Of these, a belt (not shown) is wound around a side peripheral wall portion of the rotor 144, and the belt is also wound around a drive shaft (not shown) constituting an internal combustion engine (not shown) for a vehicle. . The rotating shaft 12 is connected to the hub 58 via the bolt 56 as described above.

The energization of the electromagnet coil 146 or the stop of the energization can be freely set. As described below,
By energizing or de-energizing the electromagnet coil 146, the rotating shaft 12 can be rotated or stopped.

The reciprocating compressor 10 according to the present embodiment is basically constructed as described above.
The operation will be described.

First, a drive shaft (not shown) constituting the vehicle internal combustion engine is rotated by energizing a vehicle internal combustion engine (not shown). As a result, the rotor 144 (see FIG. 1) is rotationally biased by the action of the belt.

Here, when the electromagnet coil 146 is not energized, the clutch plate 142 is not drawn to the rotor 144. For this reason, the clutch plate 14
Since the rotor 2 and the rotor 144 are kept separated from each other, the clutch plate 142 and the hub 58 do not rotate when the rotor 144 rotates. Therefore, the rotating shaft 12 does not rotate.

On the other hand, when the electromagnet coil 146 is energized, the clutch plate 142 is attracted to the electromagnet coil 146 by the generation of a magnetic force.
42 comes into contact with the rotor 144. Therefore, rotor 1
The rotation of the clutch plate 142 and the hub 5
8 rotates, whereby the rotating shaft 12 rotates. In this case, the swash plate 14 also rotates, which causes the piston 16 to reciprocate in the cylinder 18.

The gaseous refrigerant introduced from the evaporator (not shown) into the casing via the introduction port 34 is supplied into the cylinder 18 via a supply passage (not shown). Disk parts 74a, 7
The air reaches the intake ports 94a to 94c provided in the 4b and is stored. When the piston 16 retreats, when the pressure between the first or second disk portions 74a, 74b and the valve plates 28, 28, that is, the compression chamber becomes negative, the suction valve 98 causes the gaseous refrigerant due to the pressure difference. Is pressed.

By this pressing, the first and second loop-shaped arm portions 102a and 102b of the suction valve 98 bend, and as a result, the opening / closing portion 100 causes the first or second disc portion 74a,
74b. That is, the opening / closing unit 100 opens,
The intake ports 94a to 94c are opened.

The openable opening / closing section 100 is supported in contact with the stopper section 114 of the rivet 110. That is, in the piston 16, the stopper 114 of the rivet 110 functions as a suction valve valve stopper.

The gaseous refrigerant that has passed through the intake ports 94a and 94b (see FIG. 1) is introduced into the compression chamber, and then compressed by the forward movement of the piston 16 in the compression chamber. For example,
FIG. 1 shows a state in which the gaseous refrigerant is introduced into the compression chamber on the rear cylinder block 22 side and the gaseous refrigerant compressed in the compression chamber on the front cylinder block 24 side is drawn out.

With the compression, the pressure in the compression chamber becomes higher than the pressure in the intake ports 94a to 94c, so that the opening / closing portion 100 of the suction valve 98 is pressed toward the second disk portion 74b. As a result, the intake ports 94a to 94c are
Closed by 0. That is, when the gaseous refrigerant is compressed in the compression chamber, the intake ports 94 a to 94 c formed in the second disk part 74 b are closed by the opening / closing part 100 of the suction valve 98.

When the piston 16 reaches the dead point, the head of the rivet 110 is inserted with play in the discharge port 92 (see FIG. 9). For this reason, since the dead center of the piston 16 does not need to be retracted when the discharge valve 116 is connected with the rivet 110, the compression efficiency does not decrease.

As described above, at the discharge port 92,
The opening on the side where the head of the rivet 110 is inserted is larger than that on the chamber 40 side (see FIG. 8). Therefore, rivet 1
Immediately before the head of 10 is inserted into the discharge port 92, the gaseous refrigerant passes through the discharge port 92 and enters the chamber 40 promptly without being blocked by the valve plate 28. For this reason, cylinder 1
A rapid rise in the pressure in 8 is avoided.

By chamfering the opening of the discharge port 92 on the side where the head of the rivet 110 is inserted, the pressure of the gaseous refrigerant can be released. That is, the chamfered portion of the discharge port 92 functions as an auxiliary passage for releasing the pressure of the gaseous refrigerant.

Moreover, in this case, since the discharge port 92 has a shape similar to the head of the rivet 110, the amount of the gaseous refrigerant blocked by the valve plates 28 in the compression chamber is minimized. That is, the gaseous refrigerant compressed in the cylinder 18 is efficiently guided to the chamber 40, so that the compression efficiency is further improved.

In FIG. 1, the gaseous refrigerant supplied to the compression chamber on the side of the front cylinder block 24 of the cylinder 18 and compressed is discharged from a discharge port 92 provided in the valve plate 28. At this time, the discharge valve 116 is pressed and opened by the gaseous refrigerant, and the discharge valve valve stopper 12 is opened.
8 comes into contact with the bent portion 134 of the branch portion 132.

The gaseous refrigerant is further supplied to the outlet port 36 via the flow path 38, and then the outlet port 3
Air is supplied from 6 to a condenser (not shown).

In FIG. 1, while the gaseous refrigerant supplied to the compression chamber on the front cylinder block 24 side is compressed and led out to the chamber 40, -The gaseous refrigerant to be led out is introduced.

When the swash plate 14 performs a half rotation, the disk portion of the swash plate 14 is moved to the position shown in FIG.
And the opposite phase. As a result, the piston 16 moves to the right end in FIG. 12, whereby the gaseous refrigerant introduced into the compression chamber of the rear cylinder block 22 is compressed and led out, and the piston 16 moves to the compression chamber on the front cylinder block 24 side. A gaseous refrigerant to be compressed and led out is introduced into the air. That is, in one cylinder 18, the rotating shaft 12
The rotation causes the suction and exhaust of the gaseous refrigerant.

In the above embodiment, the discharge port 92 is tapered. However, as shown in FIG. 13, the opening on the side where the head of the rivet 110 is inserted is maximized.
A discharge port 150 of the same size on the way to the chamber 40 side
It may be. Further, as shown in FIG. 14, the corner of the chamfered portion may be a curved discharge port 152, or as shown in FIG. 15, the opening on the side where the rivet 110 is inserted may be chamfered in an arc shape. It may be the discharge port 154 that has been set.

Further, the auxiliary passage for releasing the pressure of the gaseous refrigerant is not a chamfered portion of the discharge port 92 but a groove 162 or a chamfered portion (not shown) provided in the rivet 160 as shown in FIG. It may be.

Further, a chamfered portion is provided at the discharge port 92, and the rivet 160 shown in FIG.
May be connected to the piston 16.

In any case, it is needless to say that the size of the chamfer or the groove 162 is set so that the pressure of the gaseous refrigerant is reduced to such an extent that the piston 16 and the suction valve 98 are not damaged.

Although not shown, screws may be used instead of the rivets 110.

[0070]

As described above, according to the reciprocating compressor of the present invention, the auxiliary passage is provided in at least one of the fixed member connecting the discharge port or the suction valve to the piston. . For this reason, when compressing the gaseous refrigerant or the like, the pressure of the gaseous refrigerant can be released through the auxiliary passage, so that the pressure in the cylinder can be prevented from rapidly increasing, and eventually, The effect that damage to the piston, the suction valve, and the like can be avoided is achieved.

[Brief description of the drawings]

FIG. 1 is a schematic vertical cross-sectional configuration diagram of a reciprocating compressor according to the present embodiment.

FIG. 2 is a schematic sectional view taken along line II-II in FIG.

FIG. 3 is an enlarged partial longitudinal sectional view of a main part of a piston included in the reciprocating compressor of FIG. 1;

4 is a schematic plan view of the piston shown in FIG.

FIG. 5 is a schematic front view of the piston shown in FIG. 3;

FIG. 6 is a schematic front view of a suction valve connected to the piston.

FIG. 7 is an enlarged explanatory view of a rivet connecting the suction valve of FIG. 6 to the piston.

8 is an enlarged view of a main part of the rivet of FIG. 7 and a discharge port into which the rivet is inserted when the piston reaches a dead center.

9 is an enlarged explanatory view of a main part showing a state where the rivet of FIG. 7 is inserted into the discharge port of FIG. 8;

FIG. 10 is an explanatory diagram of an overall configuration of a discharge valve arranged at an opening of a discharge port.

11 is an explanatory view of the overall configuration of a valve stopper for a discharge valve that is supported by contacting a circular portion of the discharge valve when the discharge valve of FIG. 10 is opened.

FIG. 12 is a longitudinal sectional view of an essential part showing a state in which the piston has a phase opposite to that of FIG. 1 in the cylinder.

FIG. 13 is a schematic sectional view showing a discharge port in which an auxiliary passage according to another embodiment is formed.

FIG. 14 is a schematic sectional view showing a discharge port in which an auxiliary passage according to another embodiment is formed.

FIG. 15 is a schematic sectional view showing a discharge port in which an auxiliary passage according to still another embodiment is formed.

FIG. 16 is a rivet (fixing member) in which an auxiliary passage is formed.
FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Reciprocating compressor 12 ... Rotating shaft 14 ... Swash plate 16 ... Piston 18 ... Cylinder 28 ... Valve plate 32 ... Electromagnetic clutch 34 ... Introducing port 36 ... Outgoing port 72 ... Semispherical shoe 74a, 74b ... Disk part 76 ... Taper portions 80a, 80b ... intake portions 84 ... web portions 88 ... ring-shaped seal members 92, 150, 1
52, 154 ... Discharge ports 94a to 94c ... Intake port 98 ... Suction valve 100 ... Open / close section 102a, 102
b: loop-shaped arm part 108: fixed part 110, 160 ...
Rivet 114 Stopper part 116 Discharge valve 120 Branch part 122 Circular part 128 Valve stopper for discharge valve 142 Clutch plate 144 Rotor 146 Electromagnetic coil 162 Groove

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3H003 AA03 AB07 AC03 BC03 CB01 CB08 CC11 CD02 3H076 AA07 BB10 BB21 BB28 CC12 CC17 CC20 CC31

Claims (4)

[Claims] 1. A reciprocating compressor that compresses a fluid by reciprocating a piston in a cylinder, comprising: a piston provided with a suction port; a suction valve capable of opening and closing the suction port; A fixing member connected to the piston, and a discharge port into which the fixing member is inserted when the piston reaches a dead center in the cylinder; and the piston is provided in at least one of the discharge port and the fixing member. A reciprocating compressor having an auxiliary passage for releasing pressure of gas compressed by the compressor. 2. The reciprocating compressor according to claim 1, wherein
The reciprocating compressor according to claim 1, wherein the fixing member is a rivet or a screw. 3. The reciprocating compressor according to claim 1, wherein said auxiliary passage is a chamfer provided at an inlet side of said fixed member at said discharge port. Machine. 4. The reciprocating compressor according to claim 1, wherein said auxiliary passage is a chamfer or a groove provided in said fixing member.