JPH05202875A - Rotary compressor - Google Patents

Abstract

PURPOSE:To improve volumetric efficiency by forming the outer diameter side of a cylinder at a round-shaped suction port and the inner diameter side at an elliptical suction port in a suction passage respectively, to shorten a distance between a top dead end point, to a compression start, position and to ensure a passage area. CONSTITUTION:When a roller 10 which is fitted to a crank eccentrically-rotates along the inner diameter of a cylinder 18, refrigerant flows through a cylinder chamber 18a from a suction pipe through a suction passage 19. At this time, because a part of refrigerant which is sucked into the cylinder chamber 18a at a top dead point 21 flow reversely to the suction passage 19 while the roller 10 rotates from the top dead point 21 to a compression start position 22, the capacity from the top dead point 21 to the compression start position 22 is not compressed. Because the suction port of a cylinder inner diameter surface is formed in an ellipse and the distance from the top dead point 21 to the compression start position 22 is shortened, however, the volumetric efficiency is improved. Moreover, because the longer diameter of the elliptical suction port is preset at a prescribed size, it is possible to reduce passage resistance when the refrigerant is sucked into the cylinder chamber 18a.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor mounted in a refrigerator, a room air conditioner or the like, and more particularly to an invention effective for improving the efficiency of the compressor.

[0002]

2. Description of the Related Art A conventional compressor will be described with reference to FIGS. FIG. 5 is a vertical sectional view of a conventional rotary compressor. FIG. 6 and FIG. 7 are a cross-sectional view of a main part and a perspective view showing the main part of the compressor, respectively.

In the figure, 1 is a case. The electric element 2 and the compressor element 3 are housed in the case 1. The electric element 2 is composed of a stator 4 and a rotor 5, and a shaft 6 having a crank 6a is fitted into the rotor 5. The compressor element 3 is composed of a cylinder 7, an upper bearing 8, a lower bearing 9, a roller 10, a vane 11 and a spring 12. The roller 10 is fitted in the crank 6 a and has a function of eccentrically rotating along the inner diameter of the cylinder 7. The upper bearing 8 and the lower bearing 9 are fitted on the shaft 6 and fixed to both sides of the cylinder 7 by bolts 13. The body of the cylinder 7 is made of a casting material, and the cylinder chamber 7a, the vane groove 7b, and the suction passage 7c are formed by machining. A suction pipe 14 and a discharge pipe 15 are welded to the case 1 respectively. One end of the vane 11 is in contact with the roller 10 and the other end of the vane 11 is fitted into the vane groove 7b while being pressed by the spring 12.

In the rotary compressor constructed as described above, when the electric element 2 is energized, the rotor 5 rotates, and the rotary motion is transmitted to the compression element 3 by the shaft 6 directly connected to the rotor 5. Due to the transmitted rotational movement, the roller 10 fitted in the crank 6a makes an eccentric rotational movement along the inner diameter of the cylinder 7. Due to the rotation of the roller 10, the refrigerant is sucked into the suction chamber 7d through the suction passage 7c and the compression chamber 7e.
It is compressed by and discharged into the case 1, and further discharged from the discharge pipe 15 to a refrigeration cycle [not shown].

However, the structure of the conventional compressor has the following drawbacks. That is, as shown in FIG. 6, while the roller 10 rotates from the top dead center 16 to the compression start position 17, the refrigerant sucked into the cylinder chamber 7a flows backward into the suction passage 7c and is not compressed, so that the top dead center 16 Since the volume from to the compression start position 17 is the volume that is not compressed,
This was the cause of the decrease in volumetric efficiency. Also, top dead center 1
If the inner diameter of the suction passage 7c is reduced in order to reduce the distance from 6 to the compression start position 17, the passage resistance of the refrigerant increases, resulting in a problem that the volume efficiency decreases.

Further, in another conventional example shown in FIGS. 8 and 9, the suction passage 23 is provided with a groove 26 opening to a cylinder provided on one wall surface of the vane 24 and the vane groove 25, and the compression is started from the top dead center 27. Although the structure to reduce the distance to the position 28, the vane 24 slides in the vane groove 25 while receiving the lateral load F due to the differential pressure between the suction chamber 29 and the compression chamber 30 partitioned by the vane 24. Due to the presence of the groove 26, the pressure receiving area of the sliding surface is reduced, the surface pressure between the wall surface of the vane groove 25 and the vane 24 is increased, and the oil film is broken and galling is caused, which is a problem in reliability.

Incidentally, one related to this type of compressor is, for example, JP-A-61-25982.

[0008]

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems of the prior art by reducing the compression start position angle and increasing the suction passage area to improve the volumetric efficiency and improve the capacity. The purpose is.

[0009]

The above object can be achieved by the means described below. That is, this is achieved by changing the hole shape of the suction passage on the cylinder inner diameter side from a circular shape to an elliptical shape having a major axis in the cylinder height direction.

[0010]

As described above, by making the shape of the hole of the suction passage on the cylinder inner diameter side oval, the required suction passage area can be secured and the distance from the top dead center to the compression start position can be reduced, so that the volume efficiency is improved. It is possible to improve the ability.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.
Will be explained with reference to. FIG. 1 is a vertical sectional view of a rotary compressor of the present invention. 2 and 3 are a horizontal cross-sectional view and a perspective view showing a main part of the rotary compressor, respectively, and FIG. 4 is a cross-sectional view showing a processed state of the main part of the rotary compressor.

In the figure, an electric element 2 including a stator 4 and a rotor 5, a shaft 6, a cylinder 18, an upper bearing 8, a lower bearing 9, and a roller 10 are provided in a case 1 which also serves as an oil sump.
And a compression element 2 consisting of a vane 11 and a spring 12. The shaft 6 has a crank 6a, one end of which is fixed to the rotor 5 and the other end of which is an upper bearing 8a.
And the lower bearing 9. Upper bearing 8 and lower bearing 9
Also serve as side plates of the cylinder 18, and are arranged on both sides of the cylinder 18 to form a cylinder chamber 18a. The roller 10 is fitted to the crank 6a and is attached to the cylinder chamber 1
It is stored in 8a. As shown in FIG. 2, the cylinder 18 is provided with a groove 18b, and the vane 11 is fitted in the groove 18b. The vane 11 has a function of reciprocatingly sliding in the groove 18b while one end of the vane 11 is in contact with the roller 10 and the other end is pressed by the spring 12. Reference numeral 19 is a suction passage provided in the cylinder 18. 14 is a suction pipe,
Reference numeral 15 is a discharge pipe, which are fixed to the case 1 by welding.

Next, the structure of the suction passage 19 will be described with reference to FIGS. 2, 3, and 4.

In the figure, reference numeral 20 designates a through hole formed near the inner diameter of the cylinder so as to be orthogonal to the suction passage 19. Both ends of the through hole 20 have the upper bearing 8 and the lower bearing 9 described above.
The structure is sealed by. A hole for press-fitting the suction pipe 14 is formed in the suction passage 19 from the outer diameter of the cylinder 18 by drilling. This hole is the through hole 20.
Has been drilled to the depth that communicates with. On the other hand, as shown in FIG. 4, the cylinder inner diameter side is formed by drilling from an oblique direction of the cylinder inner diameter so as to communicate with the through hole 20. Therefore, the suction passage 19 on the inner diameter side of the cylinder 18 has an elliptical shape 19a as shown in FIG.

In the rotary compressor thus constructed, when the electric element 2 is energized, the rotor 5 rotates, and the rotary motion is transmitted to the compression element 3 by the shaft 6 directly connected to the rotor 5. Due to the transmitted rotational movement, the roller 10 fitted in the crank 6a makes an eccentric rotational movement along the inner diameter of the cylinder 18, and the refrigerant is drawn from the suction pipe 15 into the suction passage 1
9 and flows into the cylinder chamber 18a. At the top dead center 21, a part of the refrigerant sucked in the cylinder chamber 18a backflows into the suction passage 19 while the roller 10 rotates from the top dead center 21 to the compression start position 22. Although the volume up to the compression start position 22 is not compressed, the suction port on the inner diameter surface of the cylinder has an elliptical shape so that the distance from the top dead center 21 to the compression start position 22 is small, so that the volume efficiency is improved and the capacity is improved. improves. Further, since the major axis of the elliptical upper suction port is configured to be 60% to 80% of the cylinder height, the suction passage area is increased even if the distance from the top dead center 21 to the compression start position 22 is reduced. You can
Since the passage resistance when the refrigerant is sucked into the cylinder chamber can be reduced, the volume efficiency is improved and the capacity is improved.

[0016]

As described above, the present invention reduces the distance from the top dead center to the compression start position by forming the suction port of the inner wall of the cylinder with a narrow hole width and forming the elongated hole elongated in the cylinder height direction. In addition, since it is configured so as to have a long and narrow hole to secure a required passage area so as not to increase the suction passage resistance of the refrigerant, there is an effect that the volumetric efficiency of the compressor is improved and the capacity is improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a rotary compressor of the present invention.

FIG. 2 is a transverse cross-sectional view of the main parts of FIG.

FIG. 3 is a perspective view showing a main part of FIG.

FIG. 4 is a cross-sectional view showing a processed state of a main part of FIG.

FIG. 5 is a vertical cross-sectional view of a conventional rotary compressor.

6 is a cross-sectional view of the main parts of FIG.

FIG. 7 is a perspective view showing a main part of FIG.

FIG. 8 is a lateral cross-sectional view of a main part of a conventional rotary compressor of another embodiment.

9 is a perspective view showing a main part of FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Case, 4 ... Stator, 5 ... Rotor, 6 ... Shaft, 7, 18 ... Cylinder, 8 ... Upper bearing, 9 ... Lower bearing, 10 ... Roller, 11 ... Vane, 12 ... Spring, 13 ... Bolt, 14 ... Suction pipe, 15 ... Discharge pipe, 16, 21 ... Top dead center, 17, 22 ... Compression start position, 7c, 19 ... Suction passage, 20 ... Through hole.

Claims (4)

[Claims] 1. A cylinder and an upper bearing and a lower bearing, which also serve as side plates of the cylinder, are arranged on both sides of the cylinder to form a cylinder chamber, and the outer diameter of the cylinder is linearly formed at the center of the cylinder height. A rotary compressor having a suction passage formed by drilling from the inner diameter to the suction passage, wherein the suction passage has a circular suction port on the outer diameter side of the cylinder and an oval suction port on the inner diameter side. .. 2. The long diameter of the oblong suction port is 1.2 to 2 times larger than the diameter of the circular suction port, and the cylinder height is 0.5 to 0.8. A rotary compressor characterized by doubling. 3. The cylinder according to claim 1 or 2, wherein the oblong suction port is formed by forming a hole through the cylinder end face so as to be orthogonal to the suction passage, and the through hole is the cylinder inner diameter. Is provided in a position not in contact with the inner diameter in the vicinity of the cylinder, and further, a drill is inserted obliquely from the cylinder inner diameter side so as to intersect with the through hole, and an elliptic suction port is formed on the cylinder inner diameter surface. Compressor. 4. The rotary compressor according to claim 3, wherein the through hole of the cylinder end face is formed at a position where it is sealed by the upper bearing and the lower bearing.