JP4081224B2 - Reciprocating compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a reciprocating compressor, and more particularly to a reciprocating compressor suitably used as a component device of an automotive air conditioner.
[0002]
[Prior art]
An automotive air conditioner 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 in the evaporator tube. As a result, the air is cooled by removing the latent heat, and the cooled air is used for cooling the interior of the automobile. On the other hand, the liquid refrigerant is vaporized to become a gaseous refrigerant.
[0003]
The gaseous refrigerant is then brought to a high temperature and high pressure state by a compressor. Then, it is sent to a condenser and condensed by being cooled by the condenser to become a liquid 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 occurs relatively easily. Then, after the liquid refrigerant is sent to the evaporator, the above-described cycle is repeated, whereby the vehicle interior is continuously cooled.
[0004]
An example of the compressor that operates as described above is a reciprocating compressor. In particular, a piston fitted to the swash plate reciprocates in the cylinder as the swash plate rotates. So-called swash plate compressors are widely used.
[0005]
As one type of such a swash plate compressor, there is known one that sends a gaseous refrigerant fed from an evaporator and introduced into a cylinder to a discharge valve side of the cylinder through an intake port provided in the piston. It has been. In this case, the discharge valve side outlet of the intake port is provided on one side wall surface in the short side direction of the piston, and a suction valve that covers the intake port is connected to the one side wall surface by a fixing member. The intake valve opens when the pressure of the gaseous refrigerant reaching the intake port exceeds a predetermined value. As a result, the gaseous refrigerant introduced between the piston and the discharge valve is compressed under the action of the piston.
[0006]
As the pressure of the gaseous refrigerant becomes equal to or higher than a predetermined value due to this compression, the discharge valve opens, and as a result, the compressed gaseous refrigerant is led out from the cylinder. This gaseous refrigerant is sent to the condenser via the outlet port of the compressor.
[0007]
[Problems to be solved by the invention]
By the way, this type of swash plate compressor does not have a valve stopper for the intake valve that restricts the opening degree of the intake valve when the intake valve is opened. Since the suction valve is connected to the one side wall surface in the short direction of the piston, when the valve stopper for the suction valve is to be installed, the installation location is necessarily the one side wall surface. However, in this case, since the intake valve stopper protrudes toward the discharge port, the dead center of the piston must be retracted as compared with the case where there is no intake valve stopper. For this reason, the malfunction that the compression efficiency of a gaseous refrigerant will fall remarkably is caused. In addition, the valve stopper for the intake valve needs to have high strength in order to support the open intake valve, but such a valve stopper is generally heavy. Therefore, a large driving force is required to reciprocate the piston provided with the intake valve stopper.
[0008]
However, if a suction valve valve stopper is not installed, it is difficult to use a suction valve made of a relatively lightweight and flexible material. This is because this kind of material may be deformed and not restored to its original shape when the gaseous refrigerant passes. For this reason, a relatively hard material is selected as the constituent material of the suction valve. In this case, however, the valve is difficult to open, so the amount of gaseous refrigerant sucked is limited, resulting in a decrease in compression efficiency. Will cause.
[0009]
Even if the intake valve is made of a relatively hard material, there is a concern that the intake valve may be deformed when a large load is applied to the intake valve for some reason. In other words, when the valve stopper for the intake valve is not installed, there is a problem that there is a concern about the durability of the intake valve.
[0010]
Therefore, Japanese Utility Model Laid-Open No. 57-184284 discloses that a disc-shaped regulating plate having two protruding flange portions is fixed to one side surface of a piston together with a suction valve, and is pressed by a gaseous refrigerant so It is described that a part of the suction valve spaced apart from the side surface is brought into contact with and supported by the flange portion of the restriction plate.
[0011]
However, the restriction plate has a very large shape, and as a result, the total weight of the piston increases as the restriction plate is fixed to the piston. As a result, the amount of work for driving the piston becomes large. For example, in the case of a compressor of an air conditioner for an automobile, there is a problem that the fuel consumption of the automobile is reduced.
[0012]
In addition, when manufacturing the restriction plate, the disc plate is punched out of the material, then the disc plate is cut to form a tongue piece, and the flange piece is formed by bending the tongue piece. Must. That is, the manufacturing process is complicated and the manufacturing cost is high.
[0013]
The present invention has been made to solve the above-described problems, and it is possible to avoid a reduction in the compression efficiency of the gaseous refrigerant and an increase in the amount of work required to drive the piston. It is an object of the present invention to provide a reciprocating compressor provided with a valve stopper for an intake valve that can be provided on the intake valve and can improve the durability of the intake valve.
[0014]
[Means for Solving the Problems]
In order to achieve the above-described object, the present invention provides a reciprocating compressor that compresses fluid by reciprocating a piston in a cylinder, and is capable of opening and closing the piston provided with a suction port and the suction port. An intake valve and a fixing member that connects the intake valve to the piston are provided, and the fixing member has a stopper portion that contacts and supports the intake valve when the intake valve is opened.
[0015]
In such a configuration, by causing the fixing member to function as a valve stopper for the intake valve, it is possible to avoid an increase in weight of the piston or a decrease in compression efficiency.
[0016]
In addition, In the present invention, Fixed part Material , Rivets or screws Kara The
[0017]
In this case, the stopper part can be provided by extending integrally from the side peripheral wall part of the head of the rivet or screw. Alternatively, a member having an annular portion may be fitted into the side peripheral wall portion of the head of the rivet or screw, and this member may be used as a stopper portion. In any case, the stopper portion can be easily provided as compared with the restriction plate described above.
[0018]
In any case, it is preferable that the corner portion of the end surface of the stopper portion on the side in contact with the suction valve is curved. As a result, it is possible to avoid damage to the intake valve when the intake valve comes into contact with the stopper portion.
[0019]
The intake valve is connected to the piston by an opening / closing portion that covers the intake port, a loop-like arm portion that extends from both ends of the opening / closing portion and is narrower than the opening / closing portion, and the fixing member. It is preferable to have a fixing part. In this case, the intake valve bends starting from the loop arm portion, and only the opening / closing portion opens and closes. For this reason, since it is only necessary to provide the stopper portion at a position corresponding to the opening / closing portion, an increase in the weight of the fixing member can be minimized.
[0020]
Furthermore, it is preferable that the fixing member is inserted into the discharge port of the cylinder when the piston reaches the dead center. This is because the dead point of the piston does not need to be retracted due to the presence of the fixing member, and therefore it is possible to avoid a decrease in compression efficiency.
[0021]
In this case, it is preferable that the shape of the discharge port is similar to the shape of the fixing member. Thereby, the quantity by which the gaseous refrigerant compressed in the cylinder is blocked by the inner wall of the cylinder is reduced as much as possible. That is, since the gaseous refrigerant is efficiently led out of the cylinder, the compression efficiency is further improved.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of a reciprocating compressor according to the present invention will be described in detail with reference to the accompanying drawings.
[0023]
A schematic cross-sectional view of a reciprocating compressor according to the present embodiment is shown in FIG. In this reciprocating compressor 10, the piston 16 fitted to the swash plate 14 is rotated as the disk-like swash plate 14 fixed to the rotary shaft 12 rotates at a predetermined angle. The cylinder 18 reciprocates. In other words, the reciprocating compressor 10 is a so-called swash plate compressor, and is suitably used as an air conditioner for automobiles to send gaseous refrigerant from the evaporator to the condenser.
[0024]
The casing of the reciprocating compressor 10 includes a rear housing 20, a rear cylinder block 22, a front cylinder block 24, and a front housing 26 connected in this order from the left in FIG. Valve plates 28 and 28 are interposed between the front cylinder block 24 and the front housing 26, respectively. The two valve plates 28, 28, the rear cylinder block 22 and the front cylinder block 24 are separated from each other at an angle of 72 °, as shown in FIG. 2 which is a schematic sectional view taken along line II-II in FIG. Five cylinders 18 are formed inside the casing. Of course, the pistons 16 are arranged in all the cylinders 18.
[0025]
A hollow cylindrical portion 30 protrudes from the center of one end surface of the front housing 26 (see FIG. 1), and an electromagnetic clutch 32 is rotatably fitted to the outer peripheral wall portion of the hollow cylindrical portion 30 via a bearing 33. Are combined. The rear cylinder block 22 has an introduction port 34 and a lead-out port 36, and the rear cylinder block 22 and the front cylinder block 24 have a chamber 40 communicating with the lead-out port 36 through a flow path 38. Has been.
[0026]
On the other hand, through holes 42, 44, 46 are formed in the rear cylinder block 22, the front cylinder block 24, and the front housing 26, respectively, and the rotary shaft 12 passes through these through holes 42, 44, 46 to enter the casing. Contained. In addition, radial bearings 48 and 48 are interposed between the through holes 42 and 44 of the rear cylinder block 22 and the front cylinder block 24 and the rotary shaft 12, respectively. The rotary shaft 12 is provided with these radial bearings 48 and 48. Are rotatably supported by the rear cylinder block 22 and the front cylinder block 24. Further, a seal member 50 seals between the through hole 46 of the front housing 26 and the rotary shaft 12.
[0027]
The through hole 46 of the front housing 26 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 portion of the rotary shaft 12 is supported by the front housing 26 by projecting out of the hollow cylindrical portion 30 through the small through hole 52. A bolt hole 54 is formed at one end of the projecting rotary shaft 12, and the rotary shaft 12 and the hub 58 constituting the electromagnetic clutch 32 are connected to each other by a bolt 56 screwed into the bolt hole 54. Yes.
[0028]
The first to fourth disks 60, 62, 64, 66 are fitted in the central portion of the rotating shaft 12, and the first thrust bearing 68, the first disk is interposed between the first disk 60 and the second disk 62. A swash plate 14 is interposed between the second disk 62 and the third disk 64, and a second thrust bearing 70 is interposed between the third disk 64 and the fourth disk 66, and is fitted to the rotary shaft 12. ing.
[0029]
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 both valve plates 28 and 28. A piston 16 is fitted to the disk portion via hemispherical shoes 72, 72. As will be described later, the piston 16 reciprocates in the cylinder 18 as the swash plate 14 rotates. To do.
[0030]
The piston 16 is substantially bilaterally symmetric as shown in FIG. The piston 16 includes first and second disk portions 74a and 74b, tapered portions 76 and 76, and hemispherical grooves 77 extending from the first and second disk portions 74a and 74b, respectively, and having a tapered diameter. , 77 are formed integrally with first and second intake portions 80a, 80b having shoe receiving portions 78, 78 and a connecting portion 82 for connecting the shoe receiving portions 78, 78 to each other. The first air intake portion 80a and the second air intake portion 80b are arranged such that the shoe receiving portions 78 and 78 face each other and are separated from each other at a predetermined interval.
[0031]
The maximum height of the connecting portion 82 is set to be slightly below the center in FIG. 3 of the hemispherical groove 77 of each shoe receiving portion 78 in order to ensure escape of the swash plate 14.
[0032]
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 disc portions 74a and 74b. The web portion 84 extends from the first disc portion 74a. It is bridged over the second disk portion 74b. That is, the first and second disk portions 74a and 74b are integrally connected to each other via the web portion 84, thereby improving the rigidity of the connecting portion 82.
[0033]
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, post-processing such as notching a portion between the shoe receiving portions 78, 78 in the web portion 84 in order to ensure escape of the swash plate 14. It is necessary.
[0034]
Grooves 86, 86 are respectively provided in the side peripheral wall portions of the first and second disk portions 74a, 74b (see FIG. 3), and ring-shaped seal members 88, 88 are fitted into the grooves 86, 86, respectively. ing. The thickness of the first and second disk portions 74a and 74b is slightly larger than the ring-shaped seal members 88 and 88.
[0035]
The first and second disk portions 74a and 74b are supported by the tapered portions 76 and 76, respectively. In this case, the weight of the piston 16 can be reduced as compared with the case where the thickness of the first and second disk portions 74a and 74b is large. The upper portions of the first and second intake portions 80a, 80b above the tapered portions 76, 76 are obtuse in the middle of the diameter reduction from the first and second disk portions 74a, 74b toward the shoe receiving portions 78, 78. A bent portion 90 is provided by being bent.
[0036]
That is, the piston 16 is reduced in weight and improved in rigidity by the first and second disk portions 74a and 74b being supported by the tapered portions 76 and 76 and the web portion 84 (see FIG. 4) being provided. Has been.
[0037]
As shown in FIG. 5 which is a front view of the piston 16, a casing (from the first and second disk portions 74a and 74b to above the tapered portions 76 and 76 of the first and second intake portions 80a and 80b) Three intake ports 94a to 94c are formed so as to penetrate the gaseous refrigerant introduced from the introduction port 34 of FIG. 1) to the discharge ports 92 and 92 formed in the valve plates 28 and 28. Yes. A suction valve 98 that can be freely opened and closed is disposed in the openings of the suction ports 94a to 94c on the first and second disk portions 74a and 74b side.
[0038]
As shown in FIG. 6, the intake valve 98 includes an opening / closing portion 100 that opens and closes the intake ports 94 a to 94 c, and outer peripheries of the first and second disk portions 74 a and 74 b that extend from both ends of the opening / closing portion 100. The first and second loop-shaped arm portions 102a and 102b curved along the first and second loop-shaped arm portions 102a and 102b, the connecting portion 104 rising from the connecting portion, and the tip of the connecting portion 104 And a rivet 110 (FIGS. 1, 3, 4, and 4) as a fixing member that is disposed and has a fixing portion 108 provided with a U-shaped hole 106, and a body portion is passed through the U-shaped hole 106. 5) is connected to both side walls of the piston 16 by fitting into rivet holes 112 (see FIGS. 1 and 3) provided in the piston 16. The suction valve 98 is always pressed toward the first and second disk portions 74a and 74b by the head of the rivet 110, thereby preventing the suction valve 98 from rotating.
[0039]
Here, as shown in FIG. 7, a stopper portion 114 is formed to protrude from the side peripheral wall portion of the head of the rivet 110. The corner portion of the end surface of the stopper portion 114 on the side where the opening / closing portion 100 abuts is curved.
[0040]
As understood from FIG. 5, the rivet 110 is fitted in the rivet hole 112 so that the stopper portion 114 faces the opening / closing portion 100 of the suction valve 98. When the opening / closing part 100 is opened, the opening / closing part 100 contacts the stopper part 114 as described later.
[0041]
The hemispherical grooves 77 and 77 (see FIG. 3) of the shoe receiving portions 78 and 78 of the first and second air intake portions 80a and 80b accommodate hemispherical portions of the hemispherical shoes 72 and 72, respectively. The plane portions 72 and 72 are opposed to each other via the first and second disk portions 74a and 74b of the swash plate 14 (see FIG. 1). 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.
[0042]
As described above, the outlets 92 and 92 for discharging the gaseous refrigerant compressed in the cylinder 18 are formed in both the valve plates 28 and 28, respectively. Each cylinder 18 and each chamber 40 of the front housing 26 and the rear housing 20 communicate with each other through these discharge ports 92 and 92.
[0043]
As shown in FIG. 8, each discharge port 92 is tapered from the cylinder 18 toward the chamber 40. Further, the shape of each discharge port 92 is similar to the head of the rivet 110 on either the cylinder 18 side or the chamber 40 side, 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.
[0044]
As shown in FIG. 10, a discharge valve 116 is disposed in the opening on the chamber 40 side of the discharge port 92. The discharge valve 116 includes an annular portion 118, five branch portions 120 extending from the annular portion 118 and spaced apart from each other by 72 °, and a circular shape formed at the tip of each branch portion 120. It has the part 122 integrally. A large through hole 124 is formed in the center of the annular portion 118, and the rotary shaft 12 is passed through the large through hole 124 in the discharge valve 116 on the front housing 26 side. In addition, 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 covers the discharge port 92 of each cylinder 18 so as to be freely opened and closed.
[0045]
As shown in FIG. 11, a discharge valve stopper 128 is disposed outside the discharge valve 116. The discharge valve valve stopper 128 includes a small annular portion 130 and five branch portions 132 that extend integrally from the small annular portion 130 and are separated from each other by 72 °. The branch portion 120 (see FIG. 10) is interposed between the valve plates 28 and 28 and the branch portion 132 of the discharge valve valve stopper 128.
[0046]
This branch portion 132 is bent toward the chamber 40 side of the front housing 26 or the rear housing 20 from a position corresponding to the boundary between the branch portion 120 and the circular portion 122 of the discharge valve 116, and A bent portion 134 that is bent toward the valve plates 28 and 28 from a position corresponding to the end portion is provided (see FIGS. 1 and 11). As will be described later, when the circular portion 122 of the discharge valve 116 is separated from the valve plates 28, 28, the circular portion 122 is supported in contact with the bent portion 134 of the discharge valve valve stopper 128. This support prevents the discharge valve 116 from being deformed.
[0047]
Further, the branch portions 132 of the valve stopper 128 for the discharge valve are all connected to each other by a large annular portion 136 integral with the branch portion 132 (see FIG. 11). A plurality of fixing portions 138 provided with bolt holes 137 are formed to project from the large annular portion 136. That is, the discharge valve valve stopper 128 interposed between the front cylinder block 24 and the front housing 26 or between the rear cylinder block 22 and the rear housing 20 passes from the front housing 26 to the rear housing through the bolt hole 137. It is positioned and fixed to the casing by bolts (not shown) connecting up to 20.
[0048]
Further, the small annular portion 130 of the discharge valve valve stopper 128 is provided with a pin hole 140 at a position corresponding to the pin hole 126 of the annular portion 118 of the discharge valve 116. The pin 125 (see FIG. 1) passing through both the pin holes 126 and 140 is screwed into the front cylinder block 24 and the front housing 26 or the rear cylinder block 22 and the rear housing 20, whereby the discharge valve 116 is attached to the casing. Positioning is fixed.
[0049]
Each chamber 40 of the rear housing 20 and each chamber 40 of the front housing 26 communicate with the flow path 38, and the flow path 38 communicates with the outlet port 36. That is, each chamber 40 communicates with the outlet port 36 through the flow path 38, and the gaseous refrigerant introduced into the reciprocating compressor 10 from the introduction port 34 is compressed by the piston 16 in the cylinder. After that, it is led out from the outlet port 36 through the discharge port 92 and the chamber 40.
[0050]
The electromagnetic clutch 32 (see FIG. 1) fitted to the outer peripheral wall portion of the hollow cylindrical portion 30 of the front housing 26 is a device for rotating or stopping the rotation shaft 12.
[0051]
The electromagnetic clutch 32 includes the hub 58 described above, a clutch plate 142 coupled to the hub 58 via a bolt 141, a rotor 144, and an electromagnetic coil 146 housed in the rotor 144. Has been. Among these, a belt (not shown) is attached to the side peripheral wall portion of the rotor 144, and the belt is also attached to a drive shaft (not shown) constituting an automobile internal combustion engine (not shown). Further, as described above, the rotary shaft 12 is connected to the hub 58 via the bolt 56.
[0052]
Energization or deactivation of the electromagnet coil 146 can be set freely. As will be described later, the rotating shaft 12 can be rotated or stopped by energizing or stopping energization of the electromagnet coil 146.
[0053]
The reciprocating compressor 10 according to the present embodiment is basically configured as described above. Next, the operation thereof will be described.
[0054]
First, by energizing an automobile internal combustion engine (not shown), a drive shaft (not shown) constituting the automobile internal combustion engine is rotated. As a result, the rotor 144 (see FIG. 1) is urged to rotate by the action of the belt.
[0055]
Here, when the electromagnet coil 146 is not energized, the clutch plate 142 is not attracted to the rotor 144. For this reason, since the clutch plate 142 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.
[0056]
On the other hand, when the electromagnet coil 146 is energized, the clutch plate 142 is attracted to the electromagnet coil 146 due to the generation of magnetic force, and as a result, the clutch plate 142 contacts the rotor 144. Accordingly, the clutch plate 142 and the hub 58 are rotated in accordance with the rotation operation of the rotor 144, and thereby the rotation shaft 12 is rotated. In this case, the swash plate 14 also rotates, thereby causing the piston 16 to reciprocate within the cylinder 18.
[0057]
Gaseous refrigerant introduced from the evaporator (not shown) into the casing through the introduction port 34 is supplied into the cylinder 18 via a supply passage (not shown), and then the first and second disk portions 74a of the piston 16 are provided. , 74b reach the intake ports 94a to 94c and are stored. When the piston 16 moves backward, when the first or second disk portion 74a, 74b and the valve plate 28, 28, that is, when the compression chamber has a negative pressure, the suction valve 98 is in a gaseous state due to the pressure difference. It is pressed by.
[0058]
At this time, the suction valve 98 bends starting from the first and second loop-shaped arm portions 102a and 102b, and as a result, the opening / closing portion 100 is separated from the first or second disk portions 74a and 74b of the piston 16. That is, the intake ports 94a to 94c are opened, and the gaseous refrigerant is introduced into the compression chamber.
[0059]
As shown in FIG. 12, the separated opening / closing portion 100 is supported in contact with the stopper portion 114 of the rivet 110. This contact support prevents the opening / closing part 100 from being opened any further, and therefore prevents the suction valve 98 from being deformed.
[0060]
Thus, in this piston 16, the stopper part 114 of the rivet 110 acts as a valve stopper for the intake valve. The rivet 110 itself has a small weight, and thus the piston 16 can be driven without requiring a large driving force.
[0061]
Further, since the intake ports 94a to 94c are provided unevenly at one end portions of the first and second disk portions 74a and 74b of the piston 16, only the opening / closing portion 100 of the intake valve 98 is opened and closed. Therefore, the volume of the stopper part 114 should just be a grade which can contact | abut to the opening-and-closing part 100 and can be supported reliably. That is, in this case, an increase in the weight of the rivet 110 accompanying the provision of the stopper portion 114 can be minimized.
[0062]
Further, in this rivet 110, since the corner portion of the end surface of the stopper portion 114 on the side in contact with the opening / closing portion 100 is curved, the opening / closing portion 100 is formed by the corner portion of the stopper portion 114 when the opening / closing portion 100 contacts. Can be avoided.
[0063]
The gaseous refrigerant introduced into the compression chamber is 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 led out. .
[0064]
Along with this compression, the pressure in the compression chamber becomes higher than the pressure in the intake ports 94a to 94c on the second disc portion 74b side, so that the opening / closing portion 100 of the suction valve 98 on the second disc portion 74b side is second. It is pressed toward the disk portion 74b. As a result, the air inlets 94 a to 94 c on the second disk part 74 b side are closed by the opening / closing part 100.
[0065]
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, it is not necessary to retreat the dead center of the piston 16 when the suction valve 98 is connected by the rivet 110, so that the compression efficiency is not lowered.
[0066]
In addition, in this case, since the discharge port 92 is similar to the head of the rivet 110, the amount of the gaseous refrigerant blocked by the valve plates 28, 28 in the compression chamber is minimized. That is, since the gaseous refrigerant compressed in the cylinder 18 is efficiently led out to the chamber 40, the compression efficiency is further improved.
[0067]
In FIG. 1, the gaseous refrigerant supplied and compressed to the compression chamber on the front cylinder block 24 side of the cylinder 18 is led out to the chamber 40 from the 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 comes into contact with the bent portion 134 of the branch portion 132 of the valve stopper 128 for the discharge valve.
[0068]
The gaseous refrigerant is further sent to the outlet port 36 via the flow path 38, and then sent to the condenser (not shown) from the outlet port 36.
[0069]
In FIG. 1, the gaseous refrigerant supplied to the compression chamber on the side of the front cylinder block 24 is compressed and led out to the chamber 40, while the gaseous refrigerant to be compressed / derived next is the rear cylinder block 22. Into the side compression chamber.
[0070]
Then, when the swash plate 14 is operated by 1/2 rotation, the disk portion of the swash plate 14 is in a phase opposite to that of FIG. 1 as shown in FIG. As a result, the piston 16 moves to the right end in FIG. 13, and the gaseous refrigerant introduced into the compression chamber on the rear cylinder block 22 side is compressed and led out, and the gaseous state that is compressed and led out next. The refrigerant is introduced into the compression chamber on the front cylinder block 24 side. That is, in one cylinder 18, the refrigerant is sucked and exhausted as the rotating shaft 12 rotates once.
[0071]
Of course, in the suction valve 98 on the first disk portion 74a side, as with the suction valve 98 on the second disk portion 74b side, the opening / closing portion 100 of the suction valve 98 is when separated from the first disk portion 74a. It is abutted and supported by the stopper portion 114 of the rivet 110. For this reason, the durability of the suction valve 98 is ensured.
[0072]
In the above-described embodiment, the stopper portion 114 formed by protruding from a part of the side peripheral wall portion of the rivet 110 has been described as an example. However, as shown in FIG. It is good also as the stopper part 152 by expanding a part of diameter. Further, as shown in FIG. 15, an annular member 156 may be fitted to the side peripheral wall portion of the rivet 154 so that the entire annular member 156 functions as a stopper portion.
[0073]
Further, although not shown, a screw may be used instead of the rivet 110.
[0074]
【The invention's effect】
As described above, according to the reciprocating compressor according to the present invention, the stopper portion is provided on the fixing member that connects the suction valve to the piston. The suction valve can be supported without inviting. For this reason, it is avoided that compression efficiency falls. In addition, the suction valve is prevented from being deformed by the stopper portion, so that the effect of improving the durability of the suction valve is achieved.
[Brief description of the drawings]
FIG. 1 is a schematic vertical sectional view of a reciprocating compressor according to an embodiment of the present invention.
FIG. 2 is a schematic cross-sectional view taken along the line II-II in 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. 3. FIG.
FIG. 5 is a schematic front view of the piston shown in FIG. 3;
FIG. 6 is a schematic front view of an intake valve connected to the piston.
7 is an enlarged explanatory view of a rivet for connecting the suction valve of FIG. 6 to the piston.
FIG. 8 is an enlarged explanatory 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 the dead point.
9 is an enlarged explanatory view of main parts showing a state where the rivet of FIG. 7 is inserted into the discharge port of FIG.
FIG. 10 is an explanatory diagram of the entire configuration of a discharge valve disposed at the opening of the discharge port.
FIG. 11 is an explanatory diagram of the overall configuration of a valve stopper for a discharge valve that abuts and supports the circular portion of the discharge valve when the discharge valve of FIG. 10 is opened.
12 is an essential part enlarged explanatory view showing a state in which the opening / closing part of the intake valve of FIG. 6 is opened and is in contact with and supported by the stopper part of the rivet of FIG. 7;
13 is a longitudinal sectional view of a main part showing a state in which a piston is in a phase opposite to that in FIG. 1 in a cylinder. FIG.
FIG. 14 is a schematic overall configuration diagram showing a fixing member having a stopper portion according to another embodiment.
FIG. 15 is a schematic overall configuration diagram showing a fixing member having a stopper portion according to another embodiment.
[Explanation of symbols]
10 ... reciprocating compressor 12 ... rotating shaft
14 ... Swash plate 16 ... Piston
18 ... Cylinder 28 ... Valve plate
32 ... Electromagnetic clutch 34 ... Introduction port
36 ... Derivation port 72 ... Hemispherical shoe
74a, 74b ... disk part 76 ... taper part
80a, 80b ... intake part 84 ... web part
88 ... Ring-shaped seal member 92 ... Discharge port
94a to 94c ... intake port 98 ... intake valve
100: Opening / closing section 102a, 102b ... Loop arm section
108 ... fixed part 110, 150, 154 ... rivet
114, 152 ... Stopper 116 ... Discharge valve
120 ... branch part 122 ... circular part
128 ... Valve stopper for discharge valve 142 ... Clutch plate
144: Rotor 146: Electromagnetic coil
156 ... annular member (stopper part)

Claims (6)

In a reciprocating compressor that compresses fluid by reciprocating a piston in a cylinder,
A piston provided with a suction port; a suction valve capable of opening and closing the suction port; and a fixing member connecting the suction valve to the piston;
The fixing member comprises a rivet or a screw having a stopper portion that abuts and supports the suction valve when the suction valve is opened ;
The reciprocating compressor is characterized in that the stopper portion extends integrally from a side peripheral wall portion of a head portion of the rivet or the screw . In a reciprocating compressor that compresses fluid by reciprocating a piston in a cylinder,
A piston provided with a suction port; a suction valve capable of opening and closing the suction port; and a fixing member connecting the suction valve to the piston;
The fixing member comprises a rivet or a screw having a stopper portion that abuts and supports the suction valve when the suction valve is opened;
The reciprocating compressor, wherein the stopper portion is a member having an annular portion, and the annular portion is fitted to a side peripheral wall portion of a head portion of the rivet or the screw. The reciprocating compressor according to claim 1 or 2 , wherein a corner portion of an end surface of the stopper portion on the side in contact with the suction valve is curved. The reciprocating compressor according to any one of claims 1 to 3 , wherein the suction valve includes an opening / closing portion that covers the suction port, and an opening / closing portion that extends from both ends of the opening / closing portion and is wider than the opening / closing portion. A reciprocating compressor having a narrow loop arm portion and a fixing portion connected to the piston by the fixing member. The reciprocating compressor according to any one of claims 1 to 4 , wherein the fixing member is inserted into a discharge port of the cylinder when the piston reaches a dead center. Compressor. 6. The reciprocating compressor according to claim 5 , wherein the shape of the discharge port is similar to the shape of the fixing member.

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