CN1280592C - Closed revolving compressor - Google Patents

Abstract

In the hermetic rotary compressor, in order to ensure the performance of the compressor with low cost and high reliability, the thickness of the partition (10) is thicker than the thickness of the cylinder (8, 8A) constituting the compression element. A suction passage (12) extending from the side opening to the center is formed in the center, branched from the suction passage (12) to both sides, forming a communication hole (13) reaching the suction chamber of each compression element, and passing through the airtight container (1) One of the suction lines is connected to the suction passage (12).

Description

Hermetic rotary compressor

technical field

The present invention relates to a hermetic rotary compressor, and more particularly to a hermetic rotary compressor used for refrigerators of air conditioners, cold air application products, and the like.

Background technique

As a conventional hermetic rotary compressor, as shown in Japanese Patent Laid-Open No. 63-134188 (Prior Art 1), this type of compressor houses a motor unit and a compression mechanism unit connected by a crankshaft in a hermetic container. , The compression mechanism part is formed by two compression elements sandwiching the partition, and the refrigerant gas is sucked into the compression element through the suction line, and is compressed and discharged into the space in the airtight container. Suction passages are formed in the cylinders constituting the two compression elements, and independent suction lines are connected to the two suction passages, respectively.

In addition, as a conventional hermetic rotary compressor, as shown in Japanese Patent Application Laid-Open No. 63-162991 (Prior Art 2), this type of compressor houses a motor unit and a compression mechanism unit connected by a crankshaft. In the airtight container, the compression mechanism part is formed by two compression elements sandwiching the partition, and the refrigerant gas is sucked into the compression element through the suction line, and discharged into the space in the airtight container after compression, and the suction line is directly connected to the compression element , connected to the suction chamber.

In the hermetic rotary compressor of prior art 1, since the suction passages are formed in two cylinders and the independent suction pipes are respectively connected to the suction passages, two suction pipes are required, resulting in a significant increase in The question of cost.

In addition, in prior art 1, since the two suction lines are juxtaposed in the axial direction, the stress concentration of the internal pressure is applied to the line connecting the two suction lines, and there is a problem that the airtight container is easily damaged. In particular, when HFC410A refrigerant is used instead of HCHC22 refrigerant, the operating pressure of the compressor becomes about 1.5 times, and the pressure in the closed container becomes 1.5 times. Therefore, in prior art 1, it is necessary to increase the compressive strength of the airtight container, and there are problems such as requiring special measures such as increasing the plate thickness and improving the rigid shape.

In addition, in prior art 1, when the suction line is connected to the suction passage of the cylinder, a sliding force acts relatively between the bearing fixed to the airtight container and the cylinder, so that there is a special need to prevent mutual displacement. assembly process issues.

On the other hand, in the hermetic rotary compressor of the prior art 2, since the thickness of the cylinder constituting the compression element is extremely thin and is less than half of the thickness of the partition, when the suction passage is formed in the partition, the suction passage The cross-sectional area of the flow path becomes smaller, which increases the suction resistance of the refrigerant gas and degrades the performance of the compressor.

In addition, in Conventional Art 2, no specific suction passage structure for improving performance is provided.

A first object of the present invention is to provide a hermetic rotary compressor capable of securing compressor performance at low cost and high reliability.

A second object of the present invention is to provide a hermetic rotary compressor in which reliability can be improved and performance of the compressor can be improved.

A third object of the present invention is to provide a hermetic rotary compressor capable of securing compressor performance and improving productivity.

Moreover, the object of the present invention is not limited thereto, and other objects and advantages can be understood from the following description.

Contents of the invention

In order to achieve the above-mentioned first object, the hermetic rotary compressor of the present invention accommodates the electric motor part and the compression mechanism part connected by the crankshaft in the airtight container, and constitutes the aforementioned compression mechanism part with two compressor elements sandwiching the partition plate, The refrigerant gas is sucked into the aforementioned compression elements through the suction pipeline, and then compressed and discharged into the space of the aforementioned airtight container. The thickness of the partition plate is thicker than that of the cylinder constituting the compression element; one suction passage extending from the side opening to the center is formed in the partition plate, and a suction passage reaching the suction chamber of each compression element is formed from both sides of the suction passage branch. The communicating hole connects one of the suction lines penetrating the airtight container to the suction passage.

In order to achieve the aforementioned second object, the hermetic rotary compressor of the present invention accommodates the electric motor unit and the compression mechanism unit connected by the crankshaft in an airtight container, and the compression mechanism unit is formed by two compression elements sandwiching a partition plate, The refrigerant gas is sucked into the aforementioned compression elements through the suction pipeline, and then compressed and discharged into the space of the aforementioned airtight container. A suction passage extending from two openings in the circumferential direction of the side surface to the center is formed in the partition plate, communicates with the suction passages and forms communication holes communicating with the suction chambers of the compression elements on both sides of the branch, and passes through the above-mentioned airtight The aforementioned suction pipelines of the container are individually connected to the aforementioned suction passages.

In order to achieve the third object, the hermetic rotary compressor of the present invention accommodates the electric motor part and the compression mechanism part connected by the crankshaft in an airtight container, and forms the aforementioned compression mechanism part with two compression elements sandwiching the partition plate. The pipeline sucks the refrigerant gas into the aforementioned compression elements, and discharges it into the space of the aforementioned airtight container after being compressed. The partition plate is fixed to the airtight container by welding or the like, one suction passage extending from the side opening to the center is formed in the partition board, and one suction line is connected to the suction passage.

Description of drawings

Fig. 1 is a longitudinal sectional view showing a hermetic rotary compressor according to a first embodiment of the present invention.

FIG. 2 is a side view of FIG. 1 .

Fig. 3 is a cross-sectional view along line A-A of Fig. 1 .

Fig. 4 is a plan view of a partition used in the hermetic rotary compressor of Fig. 1 .

Fig. 5 is a B-B sectional view of Fig. 4 .

Fig. 6 is a characteristic diagram showing the volumetric efficiency of the hermetic rotary compressor of Fig. 1 in comparison with a comparative example.

Fig. 7 is a plan view showing a first modified example of the separator of Fig. 4 .

Fig. 8 is a C-C sectional view of Fig. 7 .

Fig. 9 is a top view of a second modified example of the partition in Fig. 4 .

Fig. 10 is a D-D sectional view of Fig. 9 .

Fig. 11 is a side view showing a hermetic rotary compressor according to a second embodiment of the present invention.

Fig. 12 is a view showing the spacer in the section E-E of Fig. 11 .

Fig. 13 is a sectional view taken along line F-F of Fig. 12 .

Fig. 14 is a sectional view showing a hermetic rotary compressor according to a third embodiment of the present invention.

Fig. 15 is a G-G sectional view of Fig. 14 .

Fig. 16 is a H-H sectional view of Fig. 15 .

Detailed ways

Several embodiments of the hermetic rotary compressor of the present invention will be described below using the drawings. And in each embodiment, the same member or an equivalent member is represented by the same code|symbol.

First, a hermetic rotary compressor according to a first embodiment of the present invention will be described using FIGS. 1 to 6 . Fig. 1 is a longitudinal sectional view showing the hermetic rotary compressor of the first embodiment of the present invention; Fig. 2 is a side view of Fig. 1; Fig. 3 is a sectional view of A-A of Fig. 1; Fig. 4 is a hermetic rotary compressor for Fig. 1 Fig. 5 is a B-B sectional view of Fig. 4; Fig. 6 is a characteristic diagram showing a comparison between the volumetric efficiency of the hermetic rotary compressor of Fig. 1 and a comparative example.

The hermetic rotary compressor 20 is composed of a compressor body 30 and a gas-liquid separator 2 . The hermetic rotary compressor 20 constitutes a part of the refrigerating cycle of a refrigerating machine such as an air conditioner or an air-conditioning application. As the refrigerant, an HFC-based refrigerant (for example, HFC410A refrigerant) that is better for the global environment than HCHC-based refrigerants is used.

The compressor body 30 is configured by accommodating the motor unit 21 and the compression mechanism unit 22 in the airtight container 1 . The motor unit 21 is composed of a stator 3 and a rotor 4 . The stator 3 is fixed to the container tube member 1b by shrink fit, etc.; the rotor 4 is fixed to the crankshaft 5 by press fitting or the like. At the upper and lower ends of the rotor 4, counterweights 27 are installed.

The airtight container 1 is composed of a container lower member 1a, a container cylinder member 1b, and a container upper member 1c. The container upper member 1c and the container lower member 1a are fitted into the container cylinder member 1b, and the fitting parts are welded to hermetically seal the inside. The container cylinder member 1b is formed of an iron plate into a cylindrical shape with upper and lower openings.

Compression mechanism unit 22 is composed of main bearing 7 , crankshaft 5 , sub bearing 11 , two cylinders 8 , 8A, two rollers 9 , 9 a , two blades 17 , and one separator 10 as main components. The compression mechanism part 22 has two compression elements that are composed of cylinders 8, 8A, rollers 9, 9a, and vanes 17 arranged on both sides of the partition 10, and main bearings 7 and sub-bearings 11 arranged outside them. In this way, the separator 10 is shared between the two compression elements.

The compression chamber of one compression element is constituted by the diaphragm 10, cylinder 8, main bearing 7, and roller 9; the compression chamber of the other compression element is constituted by the diaphragm 10, cylinder 8A, sub-bearing 11, and roller 9A.

The main bearing 7 is fixed to the container cylinder member 1 b by welding or the like, and the crankshaft 5 is rotatably fitted into the main bearing 7 . Two eccentric portions shifted by 180 degrees of eccentricity are formed on the crankshaft 5 , and rollers 9 and 9A are rotatably fitted to the two eccentric portions. The cylinder 8 and the partition 10 are fixed by screws 6 relative to the main bearing 7; the cylinder 8A and the partition 10 are fixed by screws 6A relative to the sub-bearing 11 . Accordingly, the two compression elements are fixed to the airtight container 1 via the main bearing 7 .

Vanes 17 are slidably fitted into the vane grooves of the cylinders 8 and 8A (see FIG. 3 ). The vane 17 is pushed by the spring 18 to divide each compression chamber into a low-pressure chamber 25 and a high-pressure chamber 26 . The urging force of the spring 18 is set to a force of a magnitude that is balanced with the inertial force generated by the reciprocating motion on the rollers 9 and 9A. In addition, a cylinder suction port 14 is provided in each low-pressure chamber 25 .

In the partition plate 10, one suction passage 12 extending from the side opening toward the center is formed. In addition, in the partition plate 10, a communication hole 13 that branches from the suction passage 12 to both sides to the cylinder suction port 14 of the suction chamber 25 of each compression element is also formed. The communication hole 13 can be formed extremely easily since the partition plate 10 is formed vertically. The flow path of the refrigerant in the separator 10 is formed by the suction passage 12 and the communication hole 13, and the flow path is vertically symmetrical.

In order to increase the flow cross-sectional area of the suction passage 12, the thickness of the partition plate 10 is formed thicker than that of the cylinders 8, 8A.

In particular, in order to make the flow passage cross-sectional area of the suction passage larger than the suction passages respectively provided on the two cylinders as in prior art 1, in this embodiment, the thickness of the partition plate 10 is formed to be the thickness of the cylinders 8, 8A. More than 1.25 times.

That is, assume that the thickness of the cylinder in prior art 1 is t, the minimum dimension from the outer circumference of the suction line to the outside of the cylinder is _t1 , the thickness of the suction line is _t2 , and the thickness of the separator 10 in this embodiment is T, The minimum dimension from the outer circumference of the suction line to the outside of the cylinder is t ₁ , and the thickness of the suction line is t ₂ . In order to make the flow cross-sectional area of the suction passage 12 larger than that of prior art 1, the following formula must be satisfied: son. In the formula, t ₁ and t ₂ can be assumed to be roughly 0.1t.

2×[π(t-4×0.1t) ² /4]<π(T-4×0.1t) ² /4 (1)

Arrangement of this formula (1) becomes 1.25t<T. In this embodiment, 1.275t=T is set.

When the thickness of the partition plate 10 is increased as described above, since the vibration of the compression mechanism portion 22 is increased, counterweights 27 having a size corresponding thereto are attached to the upper and lower ends of the rotor 4 .

The gas-liquid separator 2 is fixed to the side of the airtight container 1 by straps or the like. The upper side of the gas-liquid separator 2 has a gas-liquid separator suction port 15 . The refrigerant pipe 2 a extending from the lower side of the gas-liquid separator 2 is connected to the suction passage 12 of the separator 10 through a connecting pipe 23 and a sealing member 24 . The connecting pipe 23 is formed by airtightly welding the outer connecting pipe and the inner connecting pipe. The outer nozzle is airtightly welded to the airtight container 1, and the inner nozzle is welded to the refrigerant pipe 2a. In addition, the sealing member 24 is fitted into the suction passage 12 of the separator 10 . In FIG. 1 , the portion of the refrigerant pipe 2 a press-fitted into the sealing member 24 is omitted.

In this way, the suction line penetrating through the airtight container 1 is constituted by the refrigerant pipe 2a, the connecting pipe 23, the sealing member 24, and the like. Now, a specific method of forming the suction line will be described. The inner connection pipe and the outer connection pipe are copper-brazed to form a connecting pipe 23 . Next, the connection pipe 23 is fitted to the refrigerant pipe 2a, and copper brazing is performed between the inner connection pipe and the refrigerant pipe. On the other hand, although not shown, the sealing member 24 has its inlet side expanded so that it can be easily inserted into the refrigerant pipe 2a. When the partition plate 10 is assembled in the airtight container 1 , the refrigerant pipe 2 a is pressed into the sealing member 24 , and at the same time, the outer joint is brought into contact with a hole (not shown) in the airtight container 1 . Electrodes are placed on the contacted outer tubes, and the outer connecting tubes and the airtight container 1 are electrically welded, whereby the outer connecting tubes and the airtight container 1 are airtightly fixed. For this purpose, the formation of the suction line is finally completed.

Now, the operation of the above-mentioned hermetic compressor 20 will be described.

When the electric motor 21 is energized, the rotor 4 is rotated by receiving the rotational force from the stator 3, and the crankshaft 5 fixed to the rotor 4 rotates. The two eccentric parts of the crankshaft 5 rotate to make the two rollers 9 and 9A rotate eccentrically in the compression chamber, and at the same time, the blade 17 reciprocates in the blade groove. As a result, the refrigerant gas separated into gas and liquid by the gas-liquid separator 2 is sucked into each of the low-pressure chambers 25 of the two compression elements, and then moves to the high-pressure chamber 26, and the high-pressure refrigerant gas is discharged into the airtight container 1 from the discharge port. Inside.

Now, the suction flow of the refrigerant gas will be specifically described. The refrigerant gas sucked from the suction pipeline is branched to both sides in the communication hole 13 from the suction passage 12 as shown by the arrow 19, and sucked into the low-pressure chamber 25 through the cylinder suction ports 14, 14A.

In this compression operation, since HFC-based refrigerant is used as the refrigerant, compared with using HCFC-based refrigerant, the discharge pressure can generally be 1.5 times higher, thereby filling the space in the airtight container 1 with 1.5. pressure doubled refrigerant gas. The high-pressure refrigerant gas in the airtight container 1 is discharged to an external high-pressure pipe through a discharge pipe 16 attached to the container upper member 1c by welding or the like.

The results of comparing the volumetric efficiency in the case of connecting one suction line to the separator 10 in this example and the conventional technology 1 in which two suction lines are connected to two cylinders are shown in FIG. 6 express. From FIG. 6 , it can be confirmed that the former volumetric efficiency shown in FIG. 6( a ) can obtain performance substantially equivalent to the latter volumetric efficiency shown in FIG. 6( b ).

In the above-mentioned present embodiment, since the thickness of the partition plate 10 is thicker than the thickness of the cylinder 8 constituting the compression element to form the suction passage 12, even if it is a single suction passage 12, the cross-sectional area of the flow passage can be ensured to be enlarged. It can reduce the suction resistance of the refrigerant gas and improve the performance of the compressor. In addition, due to the formation of a suction pipeline through the airtight container 1, compared with the prior art 1, the suction pipeline can be halved, the structure is simple, and it is expected to reduce costs such as material costs, assembly and processing costs, and at the same time, no Stress concentration is formed between the two suction lines of the airtight container 1 to increase the compressive strength, thereby improving reliability. In addition, the use of HFC-based refrigerants that are good for the global environment ensures sufficient reliability.

Next, a first modification of the separator 10 of this embodiment will be described with reference to FIGS. 7 and 8 .

In this first modified example, the flow path of the partition plate 10 formed by the suction passage 12 and the communication hole 13 is substantially Y-shaped and symmetrically formed on both sides. Thus, when the refrigerant is branched from the suction passage 12 through the communication hole 13, the refrigerant is slowly branched from the suction flow direction to both sides, and the flow resistance can be lower than that of the above-mentioned embodiment. Therefore, the suction pressure loss can be reduced and the performance of the compressor can be improved. In addition, since the flow path is symmetrical on both sides, the performance of the two compression elements can be exhibited in a balanced manner without loss. In addition, since the communication hole 13 is only inclined relative to the suction passage 12, it can be relatively easily formed.

Next, a second modified example of the separator 10 of this embodiment will be described with reference to FIGS. 9 and 10 .

In this second modified example, the branch portion of the substantially Y-shaped flow path in the first modified example is formed obliquely in the direction of rotation of the crankshaft 5 (rotational direction of the roller 9 ). Accordingly, when the refrigerant is branched from the suction passage 12 to the communication hole 13, the refrigerant is branched in the direction of being sucked into the low-pressure chamber 25 sequentially, so that the refrigerant can be smoothly sucked into the low-pressure chamber. Therefore, the suction pressure loss can be further reduced compared to the first modified example, and the performance of the compressor can be further improved.

Next, a second embodiment of the hermetic rotary compressor of the present invention will be described with reference to FIGS. 11 to 13 . This second embodiment has the following points of difference from the first embodiment, and other aspects are the same as those of the first embodiment.

The embodiments are basically the same.

In this second embodiment, a suction passage 12 extending toward the center from two openings provided in the side circumferential direction is formed in the partition plate 10 . The two suction passages 12 are formed radially, and the central portion sides of the two suction passages 12 communicate with a common communication hole 13 . The suction line including the refrigerant piping 2 a penetrates the airtight container 1 and is independently connected to each suction passage 12 .

According to this second embodiment, since there are two suction passages, the flow cross-sectional area per one suction passage 12 can be reduced compared to the first embodiment. Accordingly, the thickness of the separator 10 can be reduced. In addition, since the suction passage 12 extends radially, the distance between the openings of the suction passage 12 can be increased, and the concentrated stress between the two independent suction pipes of the airtight container 1 can be reduced. Thereby, its reliability can be improved. Furthermore, if the flow passage cross-sectional area of one suction passage 12 is made the same as that of the first embodiment, the total flow passage cross-sectional area of the two suction passages 12 can be increased, and the performance of the compressor can be improved.

In addition, since the central portions of the two radially formed suction passages 12 communicate with the common communication hole 13, a simple and inexpensive suction structure can be obtained. In addition, since the flow channel cross-sectional area of the communication hole 13 is set larger than the sum of the flow channel cross-sectional areas of the two suction passages 12, the suction resistance can be reduced.

Next, a third embodiment of the hermetic rotary compressor of the present invention will be described with reference to Figs. 14 to 16 . The third embodiment has the following differences from the first embodiment, and other aspects are similar to the first embodiment.

The embodiments are basically the same.

In this third embodiment, the partition plate 10 is fixed to the airtight container 1 . Thus, when the suction line is connected to the suction passage 12, even if the connection load of the suction line is applied to the partition plate 10, since the airtight container 1 bears the load, there will be no connection between the partition plate 10 and the cylinders 8, 8A and bearing 7. There will be no relative sliding between 11 and 11, and there will be no displacement therebetween. Therefore, no special process is required for its assembly, and dimensional accuracy can be maintained therebetween. In addition, the cylinders 8, 8A and the bearings 7, 11 are fixedly supported by the partition plate 10 with the screws 6, 6A.

In addition, one suction passage 12 extending from the side opening to the center is formed in the partition plate 10, and one suction line is connected to the suction passage 12. As shown in FIG. Based on this point, the same effect as that of the first embodiment can be achieved. In the illustrated example, the thickness of the partition plate 10 is thinner than that of the cylinders 8, 8A, but the same effect can be obtained in this point if the thickness is the same as that of the first embodiment.

The partition 10 has the same outer diameter as the inner diameter of the airtight container 1 (in the illustrated example, the entire outer circumference of the partition 10 fits the entire inner circumference of the airtight container 1), and the matched portion is welded to the airtight container at several places. In addition, in the separator 10, several lubricating oil holes 10a are formed. Lubricating oil is stored above and below the partition plate 10 through the lubricating oil hole 10a, so that the lubricating oil can be easily supplied to the entire compression mechanism.

In addition, as a modified example of the third embodiment, although not shown in the figure, the partition plate is fixed to the airtight container by welding or the like, and the suction passage extending from the two openings provided in the circumferential direction of the side surface to the center is formed on the partition plate. Suction lines penetrating the airtight container may be independently connected to the respective suction passages. Thus, the third embodiment can have the functions of the second embodiment.

As can be seen from the above description, according to the present invention, a hermetic rotary compressor capable of securing compressor performance, reducing cost, and improving reliability can be obtained.

In addition, according to the present invention, it is possible to obtain a hermetic rotary compressor capable of improving reliability and compressor performance.

Furthermore, according to the present invention, it is possible to obtain a hermetic rotary compressor capable of improving productivity while ensuring compressor performance.

Claims (7)

1. airtight shape rotary compressor, this airtight shape rotary compressor, to be accommodated in the closed container by motor part and the compression mechanical part that bent axle links, form aforementioned compression mechanical part by 2 compression key elements that clip dividing plate, by suction line refrigerant gas is sucked the aforementioned key element of respectively compressing, compressed it is discharged to space in the aforementioned closed container, it is characterized in that

Make the thickness of aforementioned separator plate thicker than the thickness of the cylinder that constitutes aforementioned compression key element, in aforementioned separator plate, form the suction path that opening from the side extends to central authorities, form the aforementioned intercommunicating pore that respectively compresses the suction chamber of key element of arrival from aforementioned suction path along separate routes to both sides, make an aforementioned suction line that runs through aforementioned closed container be connected in aforementioned suction path.

2. according to the described airtight shape rotary compressor of claim 1, it is characterized in that the thickness of aforementioned separator plate is more than 1.25 times of aforementioned cylinder thickness.

3. according to the described airtight shape rotary compressor of claim 1, it is characterized in that, is that HFC is a refrigerant as the refrigerant that is used to compress.

4. according to the described airtight shape rotary compressor of claim 1, it is characterized in that, will form with the stream that aforementioned suction path and aforementioned intercommunicating pore form and be roughly Y font, bilateral symmetry.

5. according to the described airtight shape rotary compressor of claim 1, it is characterized in that, the shunt part of aforementioned intercommunicating pore is tilted to the rotation direction of aforementioned bent axle, be communicated with the aforementioned low-pressure chamber that respectively compresses key element.

6. airtight shape rotary compressor, this airtight shape rotary compressor, to be accommodated in the closed container by motor part and the compression mechanical part that bent axle links, form aforementioned compression mechanical part with two compression key elements that clip dividing plate, by suction line refrigerant gas is sucked the aforementioned key element of respectively compressing, the compressed space that is discharged in the aforementioned closed container is characterized in that

Make the thickness of aforementioned separator plate thicker than the thickness of the cylinder that constitutes aforementioned compression key element, by welding aforementioned separator plate is fixed in aforementioned closed container, a suction path that opening is from the side extended to central authorities is formed in the aforementioned separator plate, simultaneously a suction line is connected in aforementioned suction path.

7. according to the described airtight shape rotary compressor of claim 6, it is characterized in that, will constitute the cylinder of aforementioned compression key element and bearing fixing on aforementioned separator plate by bolt.

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