JPS6258095A - Rotary compressor - Google Patents

Abstract

PURPOSE:To reduce noise of a compressor by providing a delivery cover through a partition board onto the face formed with a recess for mounting the valve of a bearing while making a hole at the position corresponding with the valve hole in the partition board. CONSTITUTION:A recess 14 for mounting a valve is formed in the counter- cylinder face 13a of a bearing 13 in a compressor mechanism and a valve for opening/closing a valve hole 14b is contained in it. A delivery cover 12 is fixed through a partition board 11 onto the counter-cylinder face 13a of the bearing 13 while a thin hole 11a is formed at the position corresponding with the valve hole 14b in the partition board 11. Since the valve mounting recess 14 and the inner chamber a delivery cover 12 can be utilized as two muffler chambers communicated through the thin hole 11, noise of a compressor can be reduced effectively.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in refrigeration equipment and the like.

BACKGROUND OF THE INVENTION In recent years, compressors used in refrigeration equipment, etc. have been shifting from reciprocating types to rotary types from the standpoint of energy saving and space saving. In these rotary compressors, the inside of the sealed case is usually the high pressure side, and the refrigerant compressed in the cylinder is once discharged into the space inside the sealed case before being discharged from the compressor to the cooling system. As a result, the pressure pulsation component of the refrigerant generated by the refrigerant being compressed within the cylinder is transmitted to the space inside the sealed case, causing air column resonance in the space inside the sealed case, which in turn causes the sealed case to vibrate. Makes a lot of noise.

Therefore, conventionally, a recess for mounting a valve is provided on the opposite cylinder surface of the υ bearing, and a partition plate having a hole at a position corresponding to the valve hole for discharging refrigerant from the cylinder provided in the recess is attached to the bearing. By interposing the concave portion between the refrigerant and the discharge chamber, the concave portion acts as a resonance chamber, and the pressure pulsation component of the compressed refrigerant is attenuated by a resonance type silencing effect, thereby reducing the noise of the compressor.

An example of the conventional rotary compressor mentioned above will be described below with reference to the drawings.

4 to 6 show an example of a conventional rotary compressor.

In the figure, 1 is a rotary compressor, 2 is a sealed case, and 3 is a stator, which is fixed to the sealed case 2 by shrink fitting. 4
is a rotor connected to the crankshaft 5. 6
is a piston, and R is a cylinder. 8 is a bearing on the rotor side, which is welded to the sealed case 2. Reference numeral 9 denotes a bearing at the end of the shaft, and a linear recess 10 for housing and mounting a valve 10a is provided on the opposite cylinder surface 9a. 1ob
is the valve hole. Reference numeral 11 denotes a partition plate interposed between the bearing 9 and the cup-shaped discharge cover 12. This partition plate 11
Therefore, the recess 10 is connected to the valve chamber 10C and the discharge cover 12.
A discharge chamber 12a is formed. Further, the partition plate 11 is provided with a hole 11a corresponding to the vicinity of the valve hole 1ob, which communicates the valve chamber 10c with the discharge chamber 12a.

The operation of the rotary compressor configured as above will be described below.

The refrigerant compressed within the cylinder T is discharged from the valve hole 1ob into the valve chamber 10c. Furthermore, the refrigerant is in the valve chamber 10.
The liquid is discharged through the hole 11a into the discharge chamber 12a through the discharge chamber 12a, and then discharged from the discharge chamber 12a into the sealed case 2.

Therefore, the pressure pulsation component of the refrigerant generated within the cylinder 7 is caused by
corresponds to the vicinity of the valve hole 1ob. Therefore, the pressure pulsation component of the refrigerant radiated into the sealed case 2 is reduced, and compressor noise can be reduced.

Problems to be Solved by the Invention However, in the above configuration, the valve chamber 10C
acts as a resonant muffler, so a frequency region (hereinafter referred to as a non-attenuated region) occurs where there is almost no silencing effect and the sound is amplified.

Therefore, in this non-damping region, the pressure pulsation component of the refrigerant cannot be damped, and the compressor noise cannot be sufficiently reduced.

In view of the above-mentioned problems, the present invention provides an extremely effective noise reduction effect without reducing compressor efficiency or adding new parts.

Means for Solving the Problems In order to solve the above problems, the rotary compressor of the present invention has the following features:
A bearing having a recess for mounting a valve on a side opposite to the cylinder and a groove communicating with the recess near the valve hole, a discharge cover disposed on the side opposite to the cylinder of the bearing, the bearing and the discharge cover. and a partition plate having a hole at a position corresponding to the valve hole and interposed between the valve hole and the valve hole.

Effect: The present invention has the above-described configuration, and by applying the silencing effect of the side branch type resonator to frequencies in the non-attenuating region of the silencing effect of the valve chamber formed by the valve mounting recess and the partition plate, a very wide range of frequencies can be achieved. This provides a silencing effect.

EXAMPLE Hereinafter, a rotary compressor according to an example of the present invention will be described with reference to the drawings. Incidentally, in order to avoid duplication of explanation, the same parts as in the conventional example are given the same reference numerals and the explanation will be omitted.

1 to 3 show an embodiment of a rotary compressor of the present invention. In the figure, reference numeral 13 denotes a bearing at the end of the shaft, and the opposite cylinder surface 13a of the bearing 13 has a recess 14 for housing and mounting a valve 14a, and a groove 16 communicating with the recess 14 near the valve hole 14b. It is provided.

Partition plate 11 interposed between bearing 13 and discharge cover 12
Otherwise, the recess 14. The grooves 15 are respectively connected to the valve chamber 1.
4C, a side branch type resonance chamber 15a is formed.

The operation of the rotary compressor configured as described above will be described below with reference to FIGS. 1 to 3.

The refrigerant compressed in the cylinder T is 1. The liquid is discharged from the valve hole 14b into the valve chamber 14C, further from the hole 11a into the discharge chamber 12a, and from the discharge chamber 12a into the space inside the sealed case 2. At this time, since the valve chamber 140 acts as a side branch type resonant muffler, the pressure pulsation component of the refrigerant is attenuated, but since it is a side branch type resonant muffler, non-damped regions periodically occur. (7. In the non-damped region, the pressure pulsation component is not damped. However, the valve chamber 14
Since a resonant type noise reduction structure is formed by the side branch type resonant chamber 15a near the valve hole 14b of C,
The pressure pulsation component that could not be damped by the non-damped region is damped. At this time, it is necessary to match the cutoff frequency of the resonance type muffler by the side branch type resonance chamber 15a to the center frequency of the non-damped region periodically generated by the valve chamber 14c. In this embodiment, the formula for the cutoff frequency of the side branch type resonator is as follows: n: 1, 2.3...c:, Sound velocity under R-12 condition 2: Length of the side branch type resonance chamber 15a Based on this, the center frequency of the non-damped region of the valve chamber 14C, which occurs periodically in experiments, is adjusted to match the cut-off frequency of the side branch type resonance chamber 15a, which occurs periodically.

As described above, according to this embodiment, the recess 14 for mounting the valve 14a and the groove 15 communicating with the recess near the valve hole 14b are provided on the anti-cylinder surface 13& of the bearing 13, and the groove 15 communicating with the recess is provided in the vicinity of the valve hole 14b. The valve hole 1 is located between the discharge cover 12 and the bearing 13, which are arranged on the side opposite to the cylinder surface 13a.
By interposing the partition plate 11 having the hole 11a at the position corresponding to the recess 14 and the partition plate 11, the resonance-type noise reduction effect of the valve chamber 14c formed by the recess 14 and the partition plate 11 could not be attenuated due to the non-attenuation region. The pressure pulsation component of the refrigerant is attenuated by the resonance type silencing effect by the side branch type resonance chamber 16a formed by the groove 15 and the partition plate 11, and the cutoff frequency is determined by a general resonator. Compared to a Helmholtz type resonator, since it depends on only one length of the resonance chamber, it is possible to achieve extremely high precision and reduce variations in the cutoff frequency due to variations during processing, without reducing the efficiency of the compressor. Moreover, an extremely wide range of noise reduction effects can be obtained without adding any new parts, and compressor noise can be extremely effectively reduced.

Effects of the Invention As described above, the present invention provides a rotary compressor in which an electric compression element is housed in a sealed case, which includes a recess for mounting a valve on the opposite side of the cylinder, and a groove communicating with the recess near the valve hole. a discharge cover disposed on the opposite cylinder surface side of the bearing, and a partition plate interposed between the bearing and the discharge cover and having a hole at a position corresponding to the valve hole. This makes it possible to obtain a very wide range of noise reduction effects without reducing the efficiency of the compressor or adding new parts, thereby reducing compressor noise very effectively.

[Brief explanation of drawings]

FIG. 1 shows a bearing for a rotary compressor showing an embodiment of the present invention.
Figure 2 is an exploded perspective view showing the partition plate and discharge cover, Figure 2 is a top view of the partition plate and bearing, Figure 3 is a sectional view of the rotary compressor using Figure 1, and Figure 4 is a conventional FIG. 6 is an exploded perspective view showing a bearing, a partition plate, and a discharge cover of a rotary compressor, FIG. 6 is a top view of the partition plate and bearing, and FIG. 6 is a sectional view of a conventional rotary compressor. 2... Sealed case, 11... Partition plate,
11a...hole, 12...discharge cover,
13... Bearing, 13a... Opposite cylinder surface, 1.4... Concave portion, 14b... Valve hole, 16... Groove. Name of agent: Patent attorney Toshio Nakao and 1 other person2'
-1 Il Tiger Open Goose 13a---Il and Siseong-myeon Fig. 4 Fig. 5 I

Claims (1)

[Claims] A sealed case housing an electric compression element, a bearing having a recess for mounting a valve on a surface opposite to the cylinder and a groove communicating with the recess near the valve hole, and a discharge disposed on the surface opposite to the cylinder of the bearing. A rotary compressor comprising: a cover; and a partition plate interposed between the bearing and the discharge cover and having a hole at a position corresponding to the valve hole.