JPH02123295A - Compressor - Google Patents

Abstract

PURPOSE:To prevent reduction of an achievement coefficient in a low speed range and a high range without losing the reliability of a compressor by providing a partition plate of a lower rigidity than a bearing member between cylinders for parting the cylinders and a plate metal frame for fixing the cylinders in a closed case. CONSTITUTION:A partition plate 30 of a lower rigidity than a bearing part material 28a provided between cylinders 24a, 24b for parting the cylinders 24a, 24b, and a plate metal frame 33 for fixing the cylinders 24a, 24b in a closed case 22 are provided. By this constitution, deformation produced by increasing the rigidity of a compressor mechanism part 24 and fixing it in the closed case 22 can be small, and a clearance of a slide part can be set small to prevent leak of gas at the time of low speed operation. In addition, by composing to suck cooling medium gas at each cylinder 24a, 24b separately, pressure loss at the time of high speed operation can be prevented. Reduction of an achievement coefficient in a low speed range and a high speed range can thus be prevented.

Description

[Detailed description of the invention] [Purpose of the invention] (Industrial application field) The present invention relates to, for example, a rotary compressor.

In particular, it relates to a compressor of the type having two cylinders.

(Prior Art) For example, as a compressor for an air conditioner, there is a rotary type compressor that compresses refrigerant gas by eccentrically rotating a roller in a cylinder. Among such rotary compressors, there is a two-cylinder type compressor in which two cylinders 2.2 are arranged in a closed case 1 to form a compression mechanism section, as shown in FIG.

That is, inside each cylinder 2.2 there is a roller 3,
3 is provided, and furthermore, one end portion 4 of a crankshaft 4 is driven by an electric motor 7 and rotated inside the rollers 3, 3.

As the crank parts 5, 5 rotate, the roller 3.3 rotates eccentrically within the cylinder 2.2 while rolling into contact with the inner peripheral surface.

Furthermore, a crescent-shaped compression chamber 8 is formed between each cylinder 2 and the roller 3. A blade (not shown) is provided in each cylinder 2 to partition the compression chamber 8 into a high pressure side and a low pressure side. This blade is
It is urged toward the roller 3 side, and moves in and out of the blade groove provided in each cylinder 2, so that its tip is always in contact with the roller 3.

Further, the two cylinders 2, 2 are separated by a partition plate 9.

Further, refrigerant gas is sucked into each of the compression chambers 8, 8.

This refrigerant gas is supplied from the gas-liquid separator 9 and flows into the compression chambers 8, 8 through a suction pipe 10 connected to the gas-liquid separator 9 and a suction passage 11 formed in the cylinder 2.2. Further, the suction passage 11 is branched into two directions at the middle part.

The refrigerant gas is split midway toward two cylinders 2.2.

Further, the cylinder is fixed to the inner peripheral surface of the sealed case 1 by arc spot welding or the like.

Each sliding part in the compression mechanism (for example, the cylinder 2
and the roller 3, between the blade groove and the blade, etc.), sufficient clearance is formed to absorb deformation that occurs during welding and to prevent liquid trapping.

By the way, with this type of compressor, the operating speed is generally controlled between a low speed range and a high speed range.

Its abilities can be adjusted. For this reason 5
In such a compressor, gas leaks from each sliding part more during low speed operation than during high speed operation.

Therefore, in order to increase the COP (coefficient of performance) in the low speed range in a 2 cylinder type compressor.

It is necessary to set the clearance of each of the above-mentioned sliding parts to be smaller than that of the one-cylinder type. In other words.

Since the number of sliding parts in a 2-cylinder type is approximately twice that of a 1-cylinder type, the clearance of the sliding parts for each cylinder 2 and 2 should be set small to prevent an increase in the amount of gas leakage. There is a need to.

Furthermore, during high-speed operation, the refrigerant gas supplied from the gas-liquid separator 9 is diverted in the middle of the suction passage 11, which tends to cause pressure loss and reduce capacity. Ta.

(Problems to be Solved by the Invention) As described above, in the conventional compressor, the clearance of the sliding part within the compression mechanism is large during low-speed operation.

Gas leaked easily. Furthermore, since the refrigerant gas was divided during suction, pressure loss of the refrigerant gas was likely to occur during high-speed operation, resulting in a reduction in capacity. Due to these factors, there was a problem in that the coefficient of performance was low in low speed ranges and high speed ranges.

An object of the present invention is to provide a highly reliable compressor that has a high coefficient of performance in both the low speed range and the high speed range.

[Structure of the Invention] (Means and Effects for Solving the Problems) In order to achieve the above object, the present invention provides a sealed case and a gas-liquid separator for supplying refrigerant gas disposed within the sealed case, each of which is independent of the other. two cylinders that communicate with each other, and a crankshaft with a variable rotation speed whose crank portion is placed within these cylinders.

a bearing member that supports the crankshaft and is coupled to the cylinder; a partition plate that is provided between the cylinders and partitions both the cylinders and has lower rigidity than the bearing member; and a sheet metal frame that fixes the cylinder within the sealed case. The reason is that it is equipped with the following.

By doing this, the present invention increases the rigidity of the compression mechanism to reduce deformation caused by being fixed to the sealed case, and allows the clearance of the sliding part to be set small to reduce gas flow during low-speed operation. Made to prevent leaks. Additionally, refrigerant gas is sucked into each cylinder independently to prevent pressure loss during high-speed operation.

and.

This prevents the coefficient of performance from decreasing in low speed and high speed ranges.

(Embodiment) An embodiment of the present invention will be described below with reference to FIGS. 1 and 2.

FIG. 1 shows an embodiment of a rotary compressor according to the present invention, and numeral 21 in FIG. 1 indicates the compressor main body.

22 indicates a closed case. An electric motor 23 is disposed in the upper part of the sealed case 22, and a compression mechanism section 25 having two cylinders 24a and 24b is disposed in the lower part. The electric motor 23 includes a stator 23a fixed to the inner peripheral surface of the sealed case 22, and a rotor 23b arranged inside the stator 23a.

Further, a crankshaft 26 is inserted into and fixed to the axial center of the rotor 23b. This crankshaft 26 passes through the insides of the two cylinders 24a and 24b arranged in a pair of upper and lower parts, and has two crank parts 27a and 2 which are formed with a phase difference of about 180 degrees.
7b is located within the cylinders 24a, 24b. and.

The crankshaft 26 is a bearing 2 as a bearing member.
8a and 28b.

Further, the bearings 28a, 28b are fitted onto the crankshaft 26, and the bearings 28a, 28b are fitted onto the crankshaft 26, and both cylinders 24a
, 24b from above and below. The upper first bearing 28a is coupled to the first cylinder 24a, also located on the upper side, with its flange portion 29a substantially in contact with the first cylinder 24a. Further, the second bearing 28b on the lower side is connected to the second cylinder 24b also located on the lower side.
The flange portions 29b and 29b are connected with each other in substantially contact with each other.

Further, a partition plate 30 is interposed between the two cylinders 24a and 24b. The rigidity of this partition plate 30 is determined by the bearing 28a.

It is set lower than the flange portions 29g and 29b of 28b. Furthermore, each of the cylinders 24a.

24b is partitioned by the partition plate 30.

Crank portion 27a of crankshaft 26.

Compression chambers 31a and 31b are formed in which the compression chambers 27b are placed. Cylindrical rollers 32a and 32b are eccentrically arranged in the compression chambers 31a and 31b. This roller 32a.

32b is the crank portion 27a of the crankshaft 26
, 27b.

Moreover, in each cylinder 24a, 24b, the compression chamber 3
A blade (not shown) is provided to partition 1a and 31b into a high pressure side and a low pressure side. This blade is biased toward the rollers 32a, 32b by a spring member or the like, and moves in and out of the blade grooves provided in the single cylinders 24a, 24b, so that the tip of the blade moves toward the rollers 32a, 32b.
It is always in contact with b.

Furthermore, the cylinders 24a and 24b are the first cylinder 24
A sheet metal frame 33 formed to extend from the top side to a
It is fixed to the closed case 21 via. That is, this sheet metal frame 33 is in contact with the upper surface of the first cylinder 24a and the inner surface of the sealed case 21. The sheet metal frame 33 is fixed to the sealed case 21 by arc spot welding. Further, the sheet metal frame 33 is integrally connected to both cylinders 24a and 24b, the partition plate 30, and the bearings 28a and 28b.

Note that the sheet metal frame 33 and both cylinders 24a.

A bolt connection or the like can be considered as a means for connecting the compression mechanism section such as 24b.

Furthermore, suction passages 34a and 34b are formed in the single cylinders 24a and 24b, respectively.

One end side of these suction passages 34a, 34b is a compression chamber 31a.
, 31b, and the other end side is open to the inner peripheral surface of the cylinder 2.
It opens on the outer peripheral surfaces of 4a and 24b. Suction vibes 35a and 35b are inserted into and connected to each of the suction passages 34a and 34b from the other end side. This suction vibe 35a.

35b has one end inserted into a gas-liquid separator 36 attached to the outside of the sealed case 22 from below, and the suction passages 34a, 34b are connected to the gas-liquid separator 36 independently. It communicates.

In such a configuration, the cylinder 24a.

Since the compression mechanism section 25 such as 24b and the partition plate 30 is fixed to the sealed case 21 via the sheet metal frame 33, the rigidity is high and deformation due to arc spot welding is small. Therefore, even though it is a two-cylinder type, the cylinder 24a.

It is possible to set small clearances at each sliding portion, such as between the rollers 24b and the rollers 32a and 32b, and between the blade groove and the blade. Therefore, even during low-speed operation, gas leakage from the above-mentioned clearances can be reduced, and as shown in FIG. 2, the C0P (coefficient of performance) in the low-speed range can be increased. Further, each cylinder 24a, 24b is connected to a gas-liquid separator 38.
Since the refrigerant gas is directly and independently sucked in, there is no pressure loss in the sucked gas, and a drop in COP during high-speed operation can be prevented. Note that the solid line A in FIG. 2 shows the characteristics of the conventional device, and the solid line B in the same figure shows the characteristics of the device of this embodiment.

Furthermore, if the clearance of each sliding part in the compression mechanism is made smaller as described above, the roller 32a,
32b, a blade (not shown), etc., may cause a liquid trapping phenomenon. However, the rigidity of the partition plate 30 is limited by the bearing 28a.

Since it is set lower than 28b, even if liquid backs up, the partition plate 30 is deformed and the liquid trapping phenomenon can be prevented.

[Effects of the Invention] As explained above, in the present invention, two cylinders are fixed to a sealed case via a sheet metal frame.

The two cylinders are connected independently to a gas-liquid separator for the refrigerant gas, and to a bearing member that supports the crankshaft and is connected to the cylinder.

The partition plate that partitions the cylinders has low rigidity.

Therefore, according to the present invention, the clearance of the sliding portion can be set small, and gas leakage during low-speed operation can be prevented. Further, the refrigerant gas can be sucked in without pressure loss. Further, there is an effect that a decrease in the coefficient of performance in low speed ranges and high speed ranges can be prevented without impairing the reliability of the compressor.

[Brief explanation of the drawing]

1 and 2 show an embodiment of the present invention,
FIG. 1 is a side sectional view showing the entire compressor. Figure 2 is a graph showing the relationship between operating range and coefficient of performance. FIG. 3 is a side sectional view showing a conventional example. 21... Compressor main body, 22... Sealed case. 24a...first cylinder, 24b...second cylinder. 25... Compression mechanism section, 26... Crankshaft. 27a, 27b--crank part, 28g,
28 b - Bearing (bearing member), 30...
Partition board. 33... Sheet metal frame, 35a, 35b... Suction vibe 936... Gas-liquid separator.

Claims (1)

[Claims] A sealed case, two cylinders arranged in the sealed case and each independently communicating with a gas-liquid separator for supplying refrigerant, a crankshaft whose rotation speed is variable and whose crank part is arranged inside these cylinders, and this crank. A bearing member that supports a shaft and is coupled to the cylinder, a partition plate that is provided between the cylinders and partitions both the cylinders and has lower rigidity than the bearing member, and a sheet metal frame that fixes the cylinder in a sealed case. compressor.