JPS62157293A - Silencer of compressor - Google Patents

Abstract

PURPOSE:To reduce pressure fluctuations by forming a passage chamber on the upper-half section of a partition plate extended horizontally at the center of a side housing, forming a resonance chamber on the lower-half section, and opening a passage guiding an operating fluid from the passage chamber near the damper chamber of the passage chamber. CONSTITUTION:A horizontally extended partition plate 150 is formed at the center of a side housing 115, a passage chamber 140 is formed on the upper-half section partitioned by this partition plate and a damper chamber 114 is formed on the lower-half section. A discharge passage 117 having an opening section 165 at the position nearest to the damper chamber 114 side in the passage chamber 140 is formed integrally with the passage chamber 140 portion. Then, the discharge refrigerent in the discharge chamber 108 flows into the passage chamber 140 via a discharge communicating passage 105 and is guided into the discharge passage 117. At this point, a resonance effect by the damper chamber 114 is obtained, pressure fluctuations of the refrigerant in the discharge chamber 108 can be widely decreased by this damper chamber 114, thus a noise reducing effect can be exerted over a wide frequency range.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a silencing device for a compressor, and is effective for use in, for example, a refrigerant compressor of an air conditioner for an automobile.

[Conventional technology]

Conventionally, various noise devices have been proposed in order to limit the discharge noise of a compressor. For example, JP-A-60-λS ρl?
In the compressor described in Publication No. 2, a silencing chamber is formed in the side housing of the compressor. However, according to the experimental studies conducted by the present inventors, a sufficient sound damping effect has not yet been achieved using only the sound damping chamber formed in the side housing. FIG. 4 shows the silencing characteristics of the silencing chamber of this conventional compressor. In other words, simply forming a silencing chamber in the side housing can produce a sufficient silencing effect at a certain frequency, as shown in Figure 4, but at a certain frequency (as shown in the figure), the silencing effect is insufficient. I couldn't get it. Therefore, in a compressor using such a silencing chamber, it was necessary to install a separate muffler for the frequency range where the silencing effect is not achieved. [Problems to be solved by the invention] The present invention addresses the above points. This was devised in consideration of the above.

Therefore, the inventors of the present invention first investigated the cause of the fact that there are regions in which the conventional silencing chamber formed in the side housing does not exhibit a silencing effect.

In conventional silencing chambers, the silencing chamber also served as a path for the flow of refrigerant, and was biased. That is, in the conventional type, the pressure pulsation of the discharged refrigerant is reduced by increasing or decreasing the cross-sectional area of the refrigerant passage.

In this way, the silencing effect was attempted to be achieved simply by increasing or decreasing the passage cross-sectional area of the passage chamber, so when the discharge pulsation reached a certain frequency (region opening), the silencing effect by increasing or decreasing the passage was insufficient. It was thought that it would not be effective.

Means for Solving 5 Problems] The present invention was devised as a result of such studies by the inventors. That is, according to the present invention, the aspect that the side housing has a noise reduction effect is common to the conventional one. However, in order to produce the silencing effect,
In the present invention, the side housing is divided into two chambers by a partition plate, and one chamber is used as a resonance chamber. That is, in the silencer of the present invention, a partition plate extending horizontally is provided in the center of the side housing, and a passage chamber is formed in the upper half of the side housing. A resonance chamber is also formed in the lower half of the side housing. A passage for leading out the working fluid from the passage chamber is configured to open in the vicinity of the damper chamber in the passage chamber.

[Effect]

With the above configuration, the silencer of the present invention has the following features:
The resonance effect of the damper chamber can be effectively exhibited.

The working fluid that has flowed through the passage chamber is forced to flow near the damper chamber. Then, it is introduced into the discharge passage from the vicinity of the damper chamber. Therefore, the pressure pulsations of the working fluid flowing through the passage chamber are summed by the damper chamber. Therefore, the pressure pulsation of the working fluid flowing out from the passage chamber into the discharge passage is significantly reduced at that stage.

〔Example〕

An embodiment of the present invention will be described below based on the drawings.

In FIG. 1, 101 is a housing, which has a cylindrical cylinder space 121 inside. The rotor 102 is eccentrically arranged in the cylinder space 121 .

The rotor 102 receives the rotational force of the automobile engine through a shaft (not shown). Further, the rotor 102 is rotatably supported along with the shaft by the housing side plates 113 and 104, so that the rotor 102 rotates within the cylinder space 121. A vane groove 122 is formed in the rotor 102, and this vane l? +¥12
A vane 106 is slidably disposed within the L.

The tip of the vane 106 comes into sliding contact with the inner surface of the cylinder space 121. Therefore, the inner surface of the cylinder space 121, the rotor 10
2 outer surface and the side surface of the vane 106 form the cylinder chamber 130.
is formed.

A suction chamber (not shown) is provided on the side of the side plate 104. The suction chamber communicates with the cylinder chamber 130 via the suction port 132. The suction port opens at a portion where the cylinder chamber 130 increases in volume. That is, when the cylinder chamber 130 increases in volume, refrigerant is sucked from the suction chamber through the suction port 104.

A discharge port 119 is opened in the housing 101 . The opening position of the discharge port 119 is the location where the volume of the cylinder chamber 130 is reduced the most. 107 is a discharge chamber housing. The discharge chamber 10 is located inside the discharge chamber housing 107.
8 is formed. The discharge chamber 108 communicates with a discharge port 119 via a discharge valve 109. Note that 110 is the discharge valve 10
This is the cover of 9.

A side housing 115 is disposed on the opposite side of the housing 101 and the side plate 113.

A discharge communication passage 105 is formed in the side plate 113, and the discharge chamber 108 and the inside of the side housing 115 communicate with each other through the discharge communication passage 105.

A temporary partition 150 extending horizontally is formed in the center of the side housing. This partition temporary 150
The side housing is partitioned into two chambers, an upper half and a lower half. A damper chamber 114 is formed in the lower half, and a passage chamber 140 is formed in the upper half. As shown in FIG. 1, a support portion 155 that supports the shaft at the rear of the rotor 102 by a bearing largely protrudes from the side housing. Therefore, the volume of the 1ffl passage chamber 140 is significantly reduced by this support portion 155. FIG. 3 shows the volume distribution within the side housing 115. As is clear from this figure, the volume of the partition +fFj,''15'O upper and lower passage chamber space 140 is significantly smaller than the volume of the damper chamber space 114 below the temporary partition 15'O.

A discharge passage 117 is integrally formed in the passage chamber 1'40 portion of the side housing 115. This discharge passage 11
As shown in FIG. 2, the passageway 7 is open at the lowermost side. In other words, the opening 165 of the discharge passage 117 is located behind the passage chamber 140, at the position closest to the damper chamber 114. The discharge passage 117 extends in the vertical direction as shown, and then communicates with a discharge service valve 118. The discharge service valve is connected to the refrigerant pipe 120, so that the refrigerant flows from the discharge passage 117 through the discharge service valve 118 and the refrigerant pipe 120 to the condenser side (not shown) of the refrigeration cycle. Note that 119 is an O-ring that maintains airtightness between the discharge service valve 118 and the side housing 115.

Next, the above-mentioned tf4 compensating compression movement will be explained. When the driving force of the automobile engine is transmitted to the shaft 103 via an electromagnetic clutch (not shown), the rotational force of the shirt 1-103 is transmitted to the rotor 102.

Since the rotor 102 is arranged eccentrically within the cylinder space 121, the rotation of the rotor 102 causes the cylinder chamber 1
30 repeats increasing and decreasing its volume.

In the suction process in which the cylinder chamber 130 increases in volume, the refrigerant in the suction chamber is sucked into the cylinder chamber 130 through the suction port 132. The refrigerant sucked into the cylinder chamber 130 is then compressed while limiting the volume of the cylinder chamber 130.

Then, it is discharged into the discharge chamber 108 from the discharge port 119 at the portion where the volume of the cylinder chamber 130 is reduced the most. In this state, the refrigerant in the discharge chamber is at high temperature and high pressure. Furthermore, since the number of cylinder chambers is equal to the number of vanes 106 formed around the rotor 102, a plurality of cylinder chambers 130 are formed within the cylinder space 121. In this example, the vane 106
Since four cylinders are arranged, four cylinder chambers are formed. Therefore, the discharge refrigerant is indirectly discharged into the discharge chamber 108 from the four cylinder chambers 130.

Therefore, the discharged refrigerant in the discharge chamber 108 is accompanied by pressure pulsations. The discharged refrigerant in the discharge chamber 108 then flows into the passage chamber 140 via the discharge communication passage 105. Therefore, passage room 1
The discharged refrigerant flowing through 40 is accompanied by pressure pulsations. The passage chamber extends in the vertical direction in the figure, and its lower end communicates with the damper chamber.

The refrigerant in the passage chamber 140 is then introduced into the discharge passage 117. Here, the opening 165 of the discharge passage 117 is the discharge chamber 1.
40, it opens closest to the damper chamber 114 side. Therefore, the discharged refrigerant in the passage chamber is forced to flow toward the damper chamber 114 side. Most of the refrigerant that has flowed toward the damper chamber 114 does not flow into the damper chamber 114 and instead flows into the discharge passage 1.
Introduced on 17th. However, the refrigerant in the passage chamber 140 is subjected to a resonance effect by the damper chamber 114 at the time it is sucked into the discharge passage 117. That is, the pressure pulsations of the refrigerant in the discharge chamber are reduced by the damper chamber 114.

FIG. 5 shows the noise reduction effect of the damper chamber 114. As shown in the figure, the damper chamber 114 of this example exhibits a noise reduction effect over a wide frequency range.

The horizontal axis in FIG. 5 indicates the frequency of pressure horn pulsation. Here, the frequency of the pressure pulsation is basically the same as the pressure pulsation of the refrigerant discharged from the discharge port 119 into the discharge chamber 108 . Therefore, this frequency is approximately equal to the product of the number of cylinder chambers and the number of rotations of the rotor 102.

The refrigerant discharged into the discharge passage 117 is then discharged from the discharge service valve 118 to the condenser side of the refrigeration cycle.

Note that in the passage chamber +40 and the damper chamber 114, lubricating oil is simultaneously separated from the refrigerant. The lubricating oil separated from the refrigerant is stored on the lower surface of the damper chamber 114.

In the above example, the partition plate 150 is integrally formed with the side housing 115, but a temporary partition may be formed on the side plate 113 side. Furthermore, the temporary partition 150 does not have to be formed as a special (currently existing member), i.e., as shown in FIG.
If the support portion 155 is formed to protrude toward the side housing 115, the support portion 155 or the like may be used as a temporary partition.

Further, in the example of above i&, the discharge passage is formed in the vertical direction of the side housing l15, but it goes without saying that the direction in which the discharge passage 117 is formed is not limited to the vertical direction. Furthermore, in the above example, the compressor of the present invention was used as a refrigerant compressor for a refrigeration system, but it can also be used for other purposes.

Furthermore, the type of compressor is not limited to the above example. That is, in the above example, a so-called vane type compressor including the rotor 102 and vanes 106 is shown, but it goes without saying that other types of compressors such as reciprocating type compressors may be used.

〔Effect of the invention〕

As explained above, in the silencer of the present invention, the side housing disposed on the side of the housing is divided into an upper part and a lower half, and the upper half is used as a passage chamber and the lower half as a damper chamber. I am using it. Therefore, according to the silencer of the present invention, the damper chamber can sufficiently exhibit the resonance effect, and the pressure pulsation of the working fluid passing through the passage chamber can be favorably reduced.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing an embodiment of the compressor of the present invention, Fig. 2 is a front view showing the side housing shown in Fig. 1, and Fig. 3 shows the internal volume distribution of the side housing shown in Fig. 2. Fig. 4 is an explanatory drawing showing the silencing characteristics of a conventional silencing chamber;
The figure is an explanatory diagram showing the silencing effect of the damper chamber shown in FIG. 1. 101...Housing, 109...Discharge 0.132
... Suction port, 115... Side housing, 140.
...Aisle room, 114...Damper room, 117...Discharge passage, 150...Temporary partition.

Claims (1)

[Claims] a housing having a cylinder chamber therein; a suction chamber that communicates with the cylinder chamber through a suction hole and sucks working fluid into the cylinder chamber; and a housing that communicates with the cylinder chamber through a discharge hole and is operated from the cylinder chamber. a discharge chamber for receiving fluid;
A side housing is provided on the side of the housing and communicates with the discharge chamber via a discharge passage, and the side housing has a partition plate extending horizontally in the center thereof, The upper half of the side housing is defined by a partition plate as a passage chamber, and the lower half of the side housing is defined as a resonance chamber. A compressor silencer that opens near the room.