JPS62284988A - Rotary type compressor - Google Patents

Abstract

PURPOSE:To reduce noise by arranging two cut parts for discharge having respectively different inclination angles on inner circumferential edges of a cylinder with the inner circumferential edges making discharge holes communicate with the inside of the cylinder. CONSTITUTION:A 1st cut 15 for discharge and a 2nd cut 16 for discharge are arranged on inner circumferential edges of a cylinder 1 with the inner circumferential edges making discharge holes 9 communicate with the inside of the cylinder 1. The inclination angles of the 1st cut 15 for discharge on a main bearing 2 side is 45 deg. or less and the inclination angle B of the 2nd cut 16 for discharge on a counter bearing 3 side is 45 deg. or more, being respectively different. Accordingly, noise can be reduced by inhibiting amplification by offsetting drawbacks of each other.

Description

Detailed Description of the Invention 3. Detailed Description of the Invention [Object of the Invention] (Field of Industrial Application) The present invention relates to a rotary compressor, and particularly to a discharge structure for compressed gas compressed in a cylinder. Regarding improvements.

(Prior Art) In particular, small refrigerators used for home use! It is well known that rotary compressors, which have higher compression efficiency, smaller torque fluctuations, and lower vibration and noise than so-called reciprocating compressors, are often used in J-room equipment or refrigerators. be. The compressor section, which is the main part of this type of compressor, is constructed as shown in FIG.

That is, in the figure, 1 is a substantially cylindrical cylinder, and both upper and lower openings thereof are closed by a main bearing 2 and a sub-bearing 3. The main bearing 2 rotatably supports the middle part of the rotation @4, and the nj bearing 3 rotatably supports the lower end part. Inside the cylinder 1, an eccentric part 4a provided integrally with a part of the rotating shaft 4 and a row 55 fitted to the eccentric part 4a are housed so as to be eccentrically rotatable. The internal space that accommodates the row 55 is
A so-called cylinder chamber 6 is surrounded by the cylinder 1, the main bearing 2, and the D1 bearing 3. A through hole 7 is provided through the cylinder 1, and a suction pipe 8 is inserted into the through hole 7. Further, a discharge hole 9 and a discharge valve recess 10 are provided in the flange portion 2a of the main bearing 2 so as to communicate with each other. Discharge valve recess 1o
A discharge valve 11 is housed in the discharge valve 11 to open and close the discharge hole 9. Reference numeral 12 denotes a discharge presser that serves as a stopper when the discharge valve 11 is opened.

As the rotating shaft 4 rotates and the roller 5 is eccentrically driven within the cylinder 6, the refrigerant gas, which is the gas to be compressed, is sucked from the suction pipe 14 into the cylinder chamber 6, and the pressure Discharge valve 11 opens. At this time, the compressed refrigerant gas is discharged through the discharge hole 9 and roughly guided to a predetermined refrigeration cycle component.

By the way, in the compressor configured in this way,
There is a strong desire to increase the internal volume of the cylinder chamber 6 without changing the outer diameter, thereby increasing the size of the model and the refrigerating capacity.

To achieve this, it is possible to increase the internal volume of the cylinder 1 and the diameter of the discharge hole 9, but at the same time, the force that the discharge valve 11 receives from the compressed refrigerant gas increases, the lift becomes longer, and the amount of distortion increases. becomes. For this reason, it is necessary to increase the plate thickness of the discharge valve 11 and to increase the tightening force of the bolts that attach it to the flange 2a. As a result, the thickness of the flange 2a into which the screw is inserted becomes thicker, increasing the top clearance, and the bending force of the discharge valve 11 increases, so the work 1 to open the valve increases, and the compressor motor Input and loss input will increase.

Therefore, a method such as that shown in, for example, Japanese Utility Model Application Publication No. 57-153795 was considered. As shown in FIG. 4, the discharge hole 9, the discharge valve recess 10, the discharge valve 11, and the one-piece retainer 12 provided in the main bearing 2 are completely similar to the flange 3a of the sub-bearing 3. It will be established. Further, the inner circumferential edge of the cylinder 1 has an inclined cross section, and the discharge hole 9
Discharge notch 13°1 that communicates between °9 and the inside of the cylinder 1
3 is provided. Note that the same parts as those shown in FIG. 3 above are given the same numbers and the description thereof will be omitted.

The discharge gas compressed in the cylinder 1 is thus diverted to the respective discharge hole 9.9 and discharged via the respective discharge valve 11.11. From this, it is possible to increase the size of the model and improve performance without increasing the diameter of each discharge hole 9.9 or the plate thickness of the discharge valve 11.11, thereby reducing top clearance and input loss. It says it can be prevented.

However, the problem here is that the discharge notch 13
, 1.3. In the above publication, there is no description of the angle θ, but in the figure, each angle is approximately 4
It is drawn at a 5° angle.

However, for example, according to Japanese Utility Model Application Publication No. 57-200689, as shown in FIG.
If the angle is 5° or more, the discharge notch 13a during the discharge process
, 13a becomes large, and the discharge pressure loss becomes large, causing a decrease in efficiency. Therefore, according to the publication, as a result of various studies and experiments, the inclination angle B of the discharge notches 13b, 13b is determined to be 45 degrees or less, as shown in FIG. In reality, the angle is limited to 10' to 35 degrees. This increases the flow path area along the streamline of the discharge notch 13b, and significantly reduces the turbulence of gas from the notch 13b to the discharge hole (not shown), resulting in pressure loss. It is said that the efficiency can be improved by reducing the amount of

However, when such an inclination angle B is set, that is, when it is 45 degrees or less, although the above-mentioned effects are obtained, there is a drawback that noise increases.

That is, the flow of gas discharged from here becomes too smooth, which tends to turn into noise caused by the gas flow. Conversely, as mentioned above, by setting the inclination angle to 45° or more,
Input tends to rise and the flow of discharged gas is not smooth. After all, there are advantages and disadvantages no matter how the inclination angle is set, and if the inclination angles of both discharge notches 13.13 are unified, the disadvantages will be amplified.

(Problems to be Solved by the Invention) In the present invention, by setting the inclination angles of the discharge notches to be the same as described above, it is possible to prevent the disadvantages from being amplified, and to make use of only the strengths of each other to reduce the The present invention aims to provide a rotary compressor that achieves high efficiency while reducing noise.

[Structure of the invention]

(Means for Solving the Problems) That is, the present invention closes the openings at both ends of a cylindrical cylinder with a main bearing and an A1 bearing, and rotatably supports a rotating shaft. Discharge holes each opened and closed by a discharge valve are provided in the flange, and a first discharge notch and a second discharge notch provided with an inclined cross section at the inner circumferential edge of the cylinder are used to open and close the respective discharge holes. The rotary compressor is characterized in that the first discharge notch and the second discharge notch have different inclination angles from each other.

(Function) By configuring in this way, the first and second discharge notches are affected by both deep and shallow inclination angles at the same time, and therefore exhibit an intermediate performance between the two and amplify their shortcomings. You can prevent them while also promoting their strengths.

(Example) An example of the present invention will be described below based on FIGS. 1 and 2. Second discharge notch 1
5. With the exception of 16, the main configuration of the 0-tally type compressor is exactly the same as that previously explained as a conventional example in FIGS. 3 and 4, so the same figure will be used and new explanation will be omitted. do.

The first and second discharge notches 15 and 16 have different inclination angles, as shown in FIG. That is, the first discharge notch 15 that communicates with the discharge hole 9 provided in the main bearing 2 has a deep inclination angle A of 45 degrees or less. In addition, a second
The discharge notch 16 had a shallow inclination angle B of 45° or more.

Therefore, during the compression operation of the compressor constructed in this way, the settings of the inclination angles A and B of the respective discharge notches 15 and 16 have both positive and negative effects at the same time. However, by at least making these discharge notches 15 and 16 at different inclination angles, the disadvantages are not amplified (and a performance intermediate between the two can be achieved.In other words, the characteristics required of the compressor can be achieved). ,
In particular, noise and input values can be matched by the combination of the inclination angles A and B of each discharge notch 15, 16, and the necessary conditions can be easily satisfied.

In the above embodiment, the inclination angle A of the first discharge notch 15 is formed deep, and the inclination angle B of the second discharge notch 16 is shallow, but the present invention is not limited to this. , it goes without saying that the angles may be opposite to each other.

〔Effect of the invention〕

As explained above, according to the present invention, by making the inclination angles of the respective discharge notches different, it is possible to prevent amplification due to cancellation of each other's locations and to promote the advantages, resulting in low noise and high We can provide an efficient rotary compressor.

[Brief explanation of drawings]

10th is a longitudinal sectional view of the main parts of the rotary compressor of the present invention,
Fig. 2 is a longitudinal sectional view further enlarging a part of the compressor, Fig. 3 is a longitudinal sectional view of a main part of a rotary compressor showing a conventional example of the present invention, and Fig. 4 is a partially enlarged longitudinal sectional view. Longitudinal sectional view, 5th
This figure and FIG. 6 are vertical sectional views in which slightly different parts are enlarged. 1... Cylinder, 4... Rotating shaft, 2... Main bearing,
3... Secondary bearing, 2a... Flange (of main bearing), 3a.
... Flange (01 bearing), 11... Discharge valve, 9...
Discharge hole, 15...first discharge notch, 16...second discharge notch. Applicant's agent Patent attorney Takehiko Suzue Figure 2 Figure 5 Figure 6

Claims (1)

[Claims] A cylindrical cylinder, a main bearing and an auxiliary bearing that close the openings at both ends of the cylinder and rotatably support a rotating shaft, and a discharge valve that is opened and closed by a discharge valve provided in the collar of the main bearing and the auxiliary bearing, respectively. a first discharge notch and a second discharge notch provided with an inclined cross section on the inner circumferential edge of the cylinder that communicates the discharge holes with the inside of the cylinder; A rotary compressor characterized in that the first discharge notch and the second discharge notch have different inclination angles.