JP2003003967A - Swinging piston type compressor and refrigeration system or air conditioner using the compressor - Google Patents

Abstract

(57) Abstract: Provided is an oscillating piston compressor having a shape for processing the outer peripheral surface of a blade-integrated piston at low cost. A piston having a shape in which a flat blade is integrally formed with a cylindrical portion is inserted into an eccentric portion of a crankshaft, and the piston is inserted into an inner peripheral surface of the cylinder.
In the oscillating piston type compressor in which the compression mechanism unit 20 that revolves with respect to a is housed together with the motor unit in the case, the range from the intersection of the flat blade 4 and the cylindrical unit 2 to the cutoff position of the suction port 14 The entirety or a part of the outer peripheral surface 3 located on the suction chamber side is formed as a dent 6 having a shape depressed from the outer peripheral surface 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating piston type compressor mainly used in an air conditioner and a refrigerating device, and more particularly to a flat plate-shaped blade for partitioning a cylinder chamber into a suction chamber and a compression chamber. The present invention relates to an oscillating piston type compressor having a shape for efficiently producing a cylindrical portion of a piston integrally formed so as to protrude, and to a refrigerating device and an air conditioner including the oscillating piston type compressor.

[0002]

2. Description of the Related Art In an oscillating piston type compressor used for an air conditioner or a refrigerating apparatus, as a conventional technique relating to a shape for efficiently producing a cylindrical portion of a piston in which a flat blade is integrally formed on the cylindrical portion. Is Japanese Patent Laid-Open No. 7-
The technology disclosed in Japanese Patent No. 269483 is known.
JP-A-7-269483 discloses a cylinder having a cylindrical inner peripheral surface, a plurality of side plates closing both ends of the cylindrical inner peripheral surface of the cylinder, the cylinder and the plurality of side plates. A roller having a cylindrical outer peripheral surface that revolves in a space surrounded by a revolving motion while always maintaining a minute gap with the cylindrical inner peripheral surface of the cylinder; and a drive unit that imparts a revolving motion to the roller. The component has a vane that further divides the closed space surrounded by the cylindrical outer peripheral surface of the roller and the side plates into a plurality of closed spaces, and a plurality of closed spaces of the plurality of closed spaces is created along with the revolution movement of the roller. A rotary compressor that compresses gas by utilizing changes in respective volumes, wherein the vane and the roller are two planes parallel to each other and a center of an outer peripheral surface of the roller. And the vane are integrated in a state of being parallel to each other, and the vane is configured to oscillate around a cylindrical axis parallel to the central axis of the cylindrical inner peripheral surface of the cylinder and oscillate around the axis. In a rotary compressor having a structure supported by the cylinder so as to allow a dynamic motion and a reciprocating motion within a plane including the one axis, the vane is provided at a vane root portion of a joint portion between the roller and the vane. The rotary compressor is characterized in that it is provided with a portion thinner than the thickness of the two parallel planes.

That is, in a rotary compressor of the type in which a vane and a roller are integrally formed, a structure in which a portion thinner than the thickness of the vane is provided at the root of the vane to facilitate processing is described.

[0004]

In the above-mentioned prior art, it is not necessary to provide a portion thinner than the thickness of the vane at the root of the vane, and to perform highly accurate processing on this portion. The vane used in the above-mentioned prior art has the same meaning as the blade of the present application, and similarly, the roller has the same meaning as the cylindrical portion, and the roller / vane has the same meaning as the piston.

The first problem in the above-mentioned conventional technique is as follows.

Since the side surface of the vane is flat and the outer circumference of the roller is cylindrical, if the structure in which the vane and the roller are simply integrated is adopted, the intersection of the vane and the roller becomes a sharp corner. The flat part of the vane and the outer peripheral surface of the roller are parts that require high precision, and it is practical to finish them by grinding separately, but grinding is done including the sharp corners where they intersect. The application was a factor that hinders the processing efficiency. This prior art is intended to improve the machining efficiency by providing a portion narrower than the width of the vane at the root of the vane and eliminating the need for machining a sharp corner.

On the outer peripheral surface of the cylindrical portion of the roller-vane integrated structure, there is a portion that does not need to be processed with high precision in terms of the function as a compressor member. However, even the part that does not require high-precision machining was formed with an arc having the same radius of curvature as the other parts, so high-precision grinding is applied to almost the entire outer peripheral surface of the cylindrical part excluding the vane part. An integrated structure of rollers and vanes was manufactured. As a result, there is a problem in that the grinding process is performed to a portion where high-precision machining is not required, the grinding process time is long, and tool wear is promoted. That is, there is a problem that the process of further omitting the process that does not need to be processed with high precision is further enhanced to improve the process efficiency and reduce the manufacturing cost.

Next, the second problem of the prior art is as follows.

In the roller-vane integrated structure, the vanes serve to partition the compression chamber into a high pressure chamber and a low pressure chamber.
Pressure acts on the vane from the high pressure chamber side toward the low pressure chamber side. For this reason, it has been described in the above prior art that the vane-roller joint is connected by a smooth curve in order to avoid stress concentration. However, the radius of curvature of this curve is maximized to improve durability. There was a problem that was not taken into consideration in the structure that caused it.

The third problem in the prior art is as follows.

As described above, stress is generated at the joint between the roller and the vane, but the stress generated on the left and right of the vane is different due to the presence of the high pressure chamber and the low pressure chamber, and the required shape of the joint between the vane and the roller is also the vane. The left and right are different. For this reason, it is desirable to adopt a shape suitable for the respective stresses on the left and right sides of the vane, but in this case, it is necessary to identify the left and right sides and incorporate them into the compressor. In other words, the front and back of the roller are present. In the above-mentioned conventional technique, there is no portion for simply distinguishing between the front and back sides, and the front and back sides are judged based on the subtle difference in the shape of the joint between the vane and the roller.

The fourth problem in the prior art is as follows.

Having the above-mentioned first to third problems,
In a refrigerator or an air conditioner equipped with a compressor that adopts a roller-vane integrated piston, there are problems in the manufacturing cost and reliability of the compressor due to the first to third problems, and therefore, the manufacturing process is the same. There were issues in cost and reliability.

The object of the present invention is to solve the above-mentioned first to fourth problems. A flat blade for partitioning the inside of the cylinder into a suction chamber and a compression chamber is integrally formed with the cylindrical portion. In an oscillating piston compressor with a formed piston, it is possible to improve productivity and reduce manufacturing costs by omitting high-precision machining of parts that do not require high precision in terms of function. To provide a compressor. Another object of the present invention is to provide a compressor in which the roundness of the tolerance portion between the blade and the cylindrical portion is further expanded to suppress stress concentration and the durability of the piston is improved.

Another object of the present invention is to provide a compressor capable of facilitating the identification of the direction in which the piston is incorporated in the compressor, improving the assemblability, and reducing the manufacturing cost.

Another object of the present invention is to provide a refrigerating device or an air conditioner which is less expensive to manufacture and has high reliability by adopting this compressor.

[0017]

In order to achieve the above-mentioned object, the present invention has a cylinder having a cylindrical inner peripheral surface, and a cylindrical portion housed in the cylinder, and swings on the cylinder. A piston integrally supported so as to be slidable in the radial direction so as to project into the cylindrical portion a flat blade partitioning the cylinder into an intake chamber and a compression chamber, and a cylindrical portion of the piston. A crankshaft that rotates an eccentric portion that is rotatably fitted to the cylindrical portion so as to revolve within the cylinder; and an end plate that supports the crankshaft and closes both end openings of the cylinder. On the outer peripheral surface of the cylindrical portion of the piston, all or part of the range facing the suction side from the tolerance portion of the flat blade and the cylindrical portion facing the suction side is made smaller than the outer peripheral surface of the cylindrical portion. I It is a swing piston type compressor, characterized in that not have been the shape of relief.

In order to achieve the above object, the present invention is characterized in that, in the oscillating piston type compressor, the piston has a rounded shape in the tolerance portion of the bail and the blade. To do.

In order to achieve the above-mentioned object, the present invention provides the oscillating piston type compressor, wherein the piston is made of a sintered alloy whose material is molded in a mold, and The feature is that the material surface is formed by a mold.

In order to achieve the above object, the present invention has a cylinder having a cylindrical inner peripheral surface, and a cylindrical portion housed in the cylinder, which is swingable in the cylinder and has a radius. And a piston integrally formed with a flat blade for partitioning the inside of the cylinder into a suction chamber and a compression chamber so as to protrude into the cylindrical portion, and the cylindrical portion of the piston inside the cylinder. A crankshaft that rotates an eccentric portion that is rotatably fitted to the cylindrical portion so as to revolve, and an end plate that supports the crankshaft and closes both end openings of the cylinder;
An oscillating piston compressor, characterized in that an end face is provided with an identification mark for determining the side to be arranged on the suction chamber side with respect to the cylinder, and the identification mark has a shape that does not protrude from the end face. .

Further, in order to achieve the above object, the present invention is that the piston is made of a sintered alloy whose material is molded by a mold, and the identification mark is a material surface molded by the mold. Is characterized by.

In order to achieve the above-mentioned object, the present invention is a refrigerating apparatus including an electric refrigerator, which is equipped with an oscillating piston type compressor having the above-mentioned features.

Further, in order to achieve the above-mentioned object, the present invention is an air conditioner including a room air conditioner characterized by comprising an oscillating piston type compressor having the above-mentioned features.

[0024]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of an oscillating piston type compressor according to the present invention will be described with reference to FIGS.

FIG. 1 is a partial sectional view showing an embodiment of an oscillating piston type compressor according to the present invention, and FIG.
The case 21 and the main bearing 23 shown in FIG.
FIG. The oscillating piston type compressor is configured by housing, in a case 21, a motor unit 22 composed of a stator 22a and a rotor 22b, and a compression mechanism unit 20 rotationally driven by the motor unit 22. . The compression mechanism section 20 includes a main bearing 23 fixed to the case 21, a cylinder 11, and a sub bearing 24. The cylinder 11 has a main bearing 23 and a sub-bearing 24 that close openings at both ends of the cylinder 11 to form a working chamber including a low pressure chamber (suction chamber) 16 and a high pressure chamber (compression chamber) 17. The eccentric portion 12a of the crankshaft 12 fastened to the rotor 22b is rotatably fitted in the cylindrical portion 2 of the piston 1. Further, a blade (flat plate-shaped projection) 4 is integrally formed at one location on the outer circumference of the cylindrical portion 2 of the piston 1, and the blade 4 is swingable by a shoe 13 provided on the cylinder 11 and slidable in the radial direction. A low-pressure chamber (suction chamber) 16 and a high-pressure chamber (compression chamber) 17 are movably supported inside the cylinder 11.
Serves as a partition. Therefore, the piston 1 is revolved in the chamber of the cylinder 11 by the blade 4, and the eccentric rotation movement of the eccentric portion 12a causes the circle to revolve, thereby repeating the suction action and the compression action.

That is, in the compression mechanism section 20, the piston 1 in which the blade 4 is integrally formed with the cylindrical section 2 is incorporated in the cylinder 11, and the piston 1 is mounted on the crankshaft 12 directly connected to the motor section 22. By the eccentric rotation of the eccentric portion 12a, the revolution movement is performed with respect to the inner surface 11a of the cylinder 11 while the rotation is stopped by the blade 4.
The inside of the cylinder 11 is partitioned into a low pressure chamber (suction chamber) 16 and a high pressure chamber (compression chamber) 17 by the blade 4 of the piston 1 and a seal portion 18, and the refrigerant sucked from the suction port 14 is Is compressed by the revolving motion of the above and is discharged from the discharge port 15 to the outside of the compression mechanism section 20. Reference numeral 25 denotes a discharge pipe provided in the case 21 and connected to the discharge port 15, and 26 denotes a suction pipe directly connected to the suction port 14 formed in the auxiliary bearing 24. Therefore,
The refrigerant sucked from the suction pipe through the suction port 14 is compressed by the compression mechanism portion 20, then discharged from the discharge port 15 into the case 21, and discharged from the discharge pipe 25 to an external refrigeration cycle (not shown). It

Due to the structure described above, the low-pressure chamber (suction chamber) 16 and the high-pressure chamber (compression chamber) 17 are formed as a pair, and the suction and compression of the refrigerant are continuously repeated. Therefore, the pressure difference between the low pressure chamber (suction chamber) 16 and the high pressure chamber (compression chamber) 17 acts on the seal portion 18, and the refrigerant leaks from the high pressure chamber (compression chamber) 17 to the low pressure chamber (suction chamber) 16. I will try. Therefore, although the piston 1 can revolve around the outer peripheral surface 3 of the piston 1 and the inner peripheral surface 11a of the cylinder 11, a minute gap, that is, a seal portion 18 for preventing leakage of the refrigerant needs to be formed. There is. Therefore, it is necessary to perform highly accurate processing on the outer peripheral surface 3 of the piston and the inner peripheral surface 11a of the cylinder 11 to form the seal portion 18, which is a minute gap in the state where the piston 1 and the cylinder 11 are combined. .

Here, in FIG. 3, the piston 1 and the cylinder 1 are shown.
The entire chamber formed by 1 indicates the range of low pressure chamber (suction chamber). In FIG. 3A, the piston 1 is a refrigerant (not shown).
Is completely discharged from the discharge port 15. In this state, the entire chamber communicates with the suction port 14, and the pressure in the entire chamber is equal to the pressure of the sucked refrigerant. FIG. 3B shows a state in which the crankshaft 12 is rotated clockwise from this position in the direction of the arrow B, and the seal portion 18 is required for the first time. Inner peripheral surface 11 of cylinder 11
In a, the outer peripheral surface 3 of the cylindrical portion of the piston 1 and the inner peripheral surface 11a of the cylinder face each other to form a seal portion 18 at a portion in the direction of the arrow B from the suction port 14. Figure 3 (b)
When the crankshaft 12 further rotates in the clockwise direction indicated by the arrow B, the seal portion 18 and the blade 4 are rotated.
Thus, the high pressure chamber and the low pressure chamber are separated, and the compression operation is started.

By the way, the piston 1 is shown in FIG.
In the state between (b), since the suction port 14 of the cylinder 11 communicates with the inside of the room, the formation of the seal portion 18 is unnecessary. On the outer peripheral surface 3 of the piston 1, even if the vicinity of the suction port 14 is an arc having the same curvature as the other portions as shown by the broken line T, FIG. 3A and FIG.
In the state between the two, the suction port 14 communicates with the entire chamber formed by the piston 1 and the cylinder 11, and the seal portion 1
8 is not formed. This means that the portion indicated by the broken line T does not have to be an arc continuous with the outer peripheral surface 3 in terms of the function as a compressor, and the portion where the seal 18 is formed and the blade 4 are formed.
In between, the outer peripheral surface 3 can adopt any shape without interfering with the inner peripheral surface 11a of the cylinder.

From this, as shown in FIGS. 3 (a) and 3 (b), the outer peripheral surface 3 of the piston 1 extends from the root of the blade 4 in the direction of the arrow B, which is opposite to the suction port. , And the barbs 6 are formed so as to be recessed more in the radial direction than the other portions. In the portion where the seal portion 18 is formed, it is necessary to finish the outer peripheral surface 3 by high-precision processing in order to form a minute gap, but by providing the barge 6, a range in which high-precision processing is required. Can be reduced. That is, by providing the burr 6, it is possible to omit highly accurate processing of the portion indicated by the broken line T.

In this way, the bung 6 is attached to the outer peripheral surface 3 of the piston.
By forming it, it becomes possible to reduce the range in which the outer peripheral surface 3 is processed with high precision, as compared with the case where the bail 6 is not provided. The barb 6 can reduce the range that requires high-precision machining that requires machining time, and can improve the machining efficiency of the piston 1. For example, when the outer peripheral surface 3 is finished by a grinding process using a grindstone (not shown), the moving distance of the grindstone can be shortened and the processing time can be shortened. Moreover, since the volume removed by the grindstone is reduced, the wear amount of the grindstone can be reduced. As an example, in a piston having a diameter of the outer peripheral surface 3 of 30 to 40 mm and a width of the blade 4 of 3 to 5 mm, the distance of the portion to be finished by grinding is reduced by 10% or more as compared with the case where the bail 6 is not provided. It becomes possible. The reduction of this distance can shorten the processing time and can improve the life of the grindstone. Providing such a piston makes it possible to provide an inexpensive swing piston compressor.

Further, the piston 1 is made of a sintered alloy which is formed by a die, and a raw material is produced. The bald 6 is formed by a die when the raw material is produced. It is not necessary to form it after manufacturing, and it is possible to further improve the working efficiency of the piston 1.

Here, the shape of the intersection of the blade 4 and the burr 6 will be described with reference to FIG. The blade 4 is loaded by a refrigerant (not shown) that is compressed in the direction of arrow C. This load causes stress at the root of the blade 4, but this stress can be mitigated by forming the intersection of the blade 4 and the bald 6 into a rounded shape. The radius of curvature R of the roundness is as large as possible within the range determined by the structural conditions such as the thickness of the cylindrical portion 2 of the piston 1 and the thickness of the blade 4, so that the stress can be further reduced. The outer peripheral surface 3 in the case where the burr 6 is not provided is indicated by a broken line T, but as compared with the case where the outer peripheral surface 3 does not have the bail 6 as shown by the broken line T, the burr 6
The distance from the opposing member can be made longer by providing, and thus the radius of curvature R can be increased. By providing the burr 6 on the outer peripheral surface 3 and forming the intersection with the blade 6 into a rounded shape in this manner, the stress generated by the gas can be further reduced.

During the process in which the piston 1 performs a compression operation, a compressive stress is generated on the compression chamber side of the root of the blade 4 and a tensile stress is generated on the suction chamber side.
As an example, in a piston with a diameter of the outer peripheral surface 3 of 30 to 40 mm and a width of the blade 4 of 3 to 5 mm,
Increasing the radius of curvature of the corner roundness at the base of the blade 4 on the compression chamber side by 1 mm reduces the maximum stress by 10 to 20%. Since this tensile stress causes damage to the blade 4, it is desirable to keep it as small as possible.
And increasing the radius of curvature of the roundness of the corner are effective in improving the durability of the piston 1. In addition, the root of the blade 4 is a portion that is prone to fatigue fracture due to the operation of repeating the compression / suction cycle as a compressor. By reducing the generated stress, the durability of the piston 1 against fatigue fracture is also improved. It becomes possible. As a result, it is possible to improve the operational reliability of the compressor.

On the other hand, in the piston 1 having the bail 6, the bail 6 must be installed in the cylinder 11 in a direction facing the suction port 14. If the piston 1 is installed upside down and the bail 6 is installed so as to face the discharge port 15, a region in which the seal portion 18 is not formed occurs in the compression process, and the refrigerant in the compression process leaks out to function as a compressor. Will not be fulfilled. Therefore, when you assemble
It is necessary to confirm the position of and then assemble. The assembling of the piston 1 is an operation of inserting the inner peripheral surface 8 into the eccentric portion 12a of the crankshaft. Since the operation is to move the piston 1 in the axial direction, it is necessary to confirm the position of the bail 6 with respect to the blade from the visual field in the axial direction. In the case of manual visual identification, the presence or absence of the baldness 6 can be visually confirmed. However, when the depth of the burr 6 is shallow, it is easy to make a mistake in the discrimination by the visual work.
Further, in the case of automatically assembling by a machine (not shown), it is necessary to automatically identify the position of the bail 6, but when the depth of the bail 6 is shallow, the direction of the end face 5 is changed. It is not easy to automatically identify the presence / absence of Karageshige 6. In particular, the piston 1 is connected to the crankshaft 12 and the cylinder 11
It is not easy to automatically check the position of the bald 6 by directly using the bald 6 after the assembly.

The method of recognizing a mark mark, that is, an identification mark from the direction of the flat end surface 5 of the piston 1 makes it possible to construct an automatic apparatus which is the cheapest and reliable. An example of this identification mark is shown in FIG. In the example of FIG.
The end face 5 of the blade 4 is provided with an identification mark 7 composed of a cylindrical recess. The identification mark 7 is formed on the opposite surface shown in FIG.
Is not provided. Identification mark 7 consisting of this cylindrical hollow
It is possible to determine the direction in which the bald 6 is to be incorporated by detecting the position before assembling. The identification mark 7 in this example is the end face 5.
It is an identification mark that can be easily and reliably identified by detecting a step between and. The identification mark 7 functions not only in the shape of this example but also in the marking or printing of shapes or characters.
Further, the identification mark 7 may have a shape having a protruding portion in the recess. Furthermore, the recess of the identification mark 7 has a function if it is not a cylindrical shape but a conical shape, a prismatic shape, or the like. The identification mark 7 provided on the end face 5 can be easily detected automatically from the direction in which the end face 5 is viewed in plan even after the piston 1 is assembled in the crankshaft 12 and the cylinder 11. It is also effective for inspection.

In the piston 1 having the identification mark 7 such as the recess as described above, the efficiency and reliability of assembly are improved, and as a result, it is possible to provide a swinging piston compressor with good productivity.

Further, the piston 1 is made of a sintered alloy which is molded by a die, and a material is produced, and the identification mark 7 is formed by a die when the material is produced. It is not necessary to form the material after printing by printing, and it is possible to provide an oscillating piston compressor with high productivity.

Here, an electric refrigerator is shown in FIG. 6 as an example of a refrigerating apparatus having an oscillating piston type compressor having the above-mentioned piston. An oscillating piston compressor 30 is provided below the electric refrigerator 40. A refrigerant (not shown) is compressed by the oscillating piston type compressor 30, and the compressed refrigerant is supplied to a pipe provided in the refrigerator 40.
The refrigeration cycle of returning to the swing piston type compressor 30 again via the condenser and the evaporator (not shown) is repeated. The refrigerant radiates heat and absorbs heat in the process of the refrigeration cycle, and the function of the refrigerator is fulfilled by the heat radiation and heat absorption of the refrigerant. With this configuration, the oscillating piston type compressor 30 includes a piston having the above-mentioned features. This piston reduces the manufacturing cost of the oscillating piston compressor 30 and improves the operational reliability. However, by providing the refrigerator 40 with the oscillating piston compressor 30 having this feature, the manufacturing cost of the refrigerator 40 can be reduced. It is possible to improve the operational reliability.

A separate room air conditioner is shown in FIG. 7 as an example of an air conditioner equipped with a swinging piston compressor having the above-mentioned piston. Room air conditioner 5
At 0, the swinging piston type compressor 3 provided in the outdoor unit 51
A refrigerant (not shown) is compressed by 0, and the compressed refrigerant is sent to the indoor unit 52 via the connection pipe 53 and returns to the outdoor unit 51 again. In the process of this cycle, the refrigerant radiates heat and absorbs heat, and the heat radiating and absorbing heat of the refrigerant fulfills the function as a room air conditioner. With this configuration, the oscillating piston type compressor 30 includes a piston having the above-mentioned features. This piston reduces the manufacturing cost of the oscillating piston compressor 30 and improves the operational reliability. However, by providing the oscillating piston compressor 30 having this feature in the room air conditioner, the manufacturing cost of the room air conditioner can be reduced. It is possible to improve the operational reliability.

[0041]

According to the present invention, since the burr is formed on the outer peripheral surface of the piston, the range in which the outer peripheral surface is machined with high accuracy can be reduced as compared with the case where there is no burr. It will be possible. Due to this, the range that requires high-precision machining that requires machining time is reduced, and it is possible to improve the machining efficiency of the piston. Machine can be provided.

A piston is formed in a mold by using a sintered alloy to make a material, and a burr is formed in the mold when the material is manufactured, so that the budge is formed by machining such as cutting or grinding after the material is manufactured. Therefore, it is possible to further improve the machining efficiency of the piston. As a result, the first problem that has conventionally occurred can be solved.

Although the base of the blade of the piston adopts a rounded shape, this roundness can alleviate the stress concentration at the root of the blade and improve the durability of the piston. As a result, it is possible to improve the operational reliability of the compressor. As a result, the second problem that has conventionally occurred can be solved.

A piston provided with a barb causes directionality in the assembling. However, when a piston provided with an identification mark for identifying this is provided on the end face, the automatic identification becomes easy and the assemblability is good. It is possible to provide a piston. This can solve the third problem that has occurred conventionally.

By adopting the oscillating piston type compressor provided with the piston having such an effect in the refrigerating apparatus, it is possible to reduce the manufacturing cost of the refrigerating apparatus and improve the operation reliability.

By adopting an oscillating piston type compressor having a piston having such an effect in an air conditioner, it is possible to reduce the manufacturing cost of the air conditioner and improve the operational reliability. This can solve the fourth problem that has occurred conventionally.

[Brief description of drawings]

FIG. 1 is a partial sectional view showing an embodiment of an oscillating piston type compressor according to the present invention.

FIG. 2 is a partial sectional view taken along the line AA of FIG.

FIG. 3 is a partial cross-sectional view showing the piston in a different position as seen from the direction of arrow AA in FIG.

FIG. 4 is a partial cross-sectional view showing an embodiment of a swing piston according to the present invention, and in particular, showing a bald shape.

FIG. 5 shows an embodiment of a swing piston according to the present invention, in particular, a perspective view and a partial cross-sectional view showing identification marks.

FIG. 6 is a perspective view showing an electric refrigerator provided with an oscillating piston type compressor according to the present invention.

FIG. 7 is a perspective view showing a room air conditioner equipped with a swinging piston type compressor according to the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Piston, 2 ... Cylindrical part, 3 ... Outer peripheral surface, 4 ... Blade, 5 ... End surface, 6 ... Bite, 7 ... Identification mark, 8 ... Inner peripheral surface, 11
… Cylinder, 11a… Inner peripheral surface, 12… Crankshaft, 12a
... eccentric part, 13 ... shoe, 14 ... suction port, 15 ... discharge port, 16 ...
Low pressure chamber, 17 ... High pressure chamber, 18 ... Seal part, 20 ... Compression mechanism part,
21 ... Case, 22a ... Stator, 22b ... Rotor, 23 ... Main bearing, 24 ... Sub bearing, 25 ... Discharge pipe, 26 ... Suction pipe,
30 ... Oscillating piston compressor, 40 ... Electric refrigerator, 50 ... Room air conditioner, 51 ... Outdoor unit, 52 ... Indoor unit, 53 ... Connection piping

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Nobuo Abe             800 Tomita, Odaira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division (72) Inventor Minoru Tateno             800 Tomita, Odaira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division (72) Inventor Tatsuo Horie             800 Tomita, Odaira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division (72) Inventor Kazuya Kato             800 Tomita, Odaira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division (72) Inventor Fumitaka Nishioka             800 Tomita, Odaira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division

Claims (7)

[Claims] 1. A cylinder having a cylindrical inner peripheral surface and a cylindrical portion housed in the cylinder, swingably supported by the cylinder and slidable in a radial direction, and sucking in the cylinder. And a piston integrally formed with a flat blade for partitioning the chamber and the compression chamber so as to project into the cylindrical portion, and rotatably fitted to the cylindrical portion so that the cylindrical portion of the piston revolves in the cylinder. A crankshaft for rotating the eccentric part to be fitted, and an end plate for supporting the crankshaft and closing both end openings of the cylinder are provided, and the flat blade and the cylindrical part of the outer peripheral surface of the cylindrical part of the piston are provided. All the parts or a part of the range facing the deadline position of the suction port facing the suction port side from the intersecting part are formed into a concave shape which is recessed toward the center side from the outer peripheral surface of the cylindrical part. Moving piss Down type compressor. 2. In the piston, the intersection of the bail and the blade has a rounded shape.
The oscillating piston type compressor according to claim 1. 3. The piston according to claim 1 or 2, wherein the piston is made of a sintered alloy whose material is formed by a die, and the burr is a material surface formed by the die.
The oscillating piston compressor according to any one of 1. 4. A cylinder having a cylindrical inner peripheral surface and a cylindrical portion housed in the cylinder, swingably supported by the cylinder and slidably in a radial direction, and sucking in the cylinder. And a piston integrally formed with a flat blade for partitioning the chamber and the compression chamber so as to project into the cylindrical portion, and rotatably fitted to the cylindrical portion so that the cylindrical portion of the piston revolves in the cylinder. A crankshaft for rotating the eccentric part to be fitted, and an end plate for supporting the crankshaft and closing both end openings of the cylinder are provided, and the piston has a side arranged on the suction chamber side with respect to the cylinder. An oscillating piston compressor, wherein an identification mark for determining is provided on an end surface of the piston, and the identification mark does not protrude from the end surface. 5. The swing piston according to claim 4, wherein the piston is made of a sintered alloy whose material is molded by a mold, and the identification mark is a material surface molded by the mold. Shape compressor. 6. A refrigerating apparatus including an electric refrigerator comprising the oscillating piston type compressor according to any one of claims 1 to 5. 7. An air conditioner including a room air conditioner, comprising the oscillating piston type compressor according to claim 1. Description: