JPH06307363A - Rotary compressor - Google Patents

Abstract

PURPOSE:To suppress the deformation of the inside structure of a pump after assembling by fixing a cylinder of a compression mechanism part to a closed container by welding, fastening the main and sub bearings to the cylinder by bolts, and at the same time, setting the bolt-tightening torque of the sub gearing to be relatively weaker by the specific value or more. CONSTITUTION:A motor part 6 and a pump part 7 are stored in an enclosed container 1. The motor part 6 consists of a stator 6a and a rotor 12. In addition, the pump part 7 consists of a rotary shaft 13, a cylinder 3, main and sub bearings 2, 4, a roller 14, vanes 15, a spring 17 or the like. The cylinder 3 is fixed to the inside structure of the enclosed container 1 by welding. On the other hand, the main and sub bearings 2, 4 are connected to each side of the cylinder 3 by tightening the respective individual bolts 5 to support the rotary shaft 13. The tightening torque of the respective bolts 5 is set, e.g. to be 80-100 kgf.cm on the main bearing 2 side, and 70-90 kgf. cm on the sub bearing 4 side, and the sub bearing 4 side is tightened weaker by 10kgf. cm in average.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used in, for example, a refrigeration cycle for an air conditioner or a refrigerator, and more particularly to a rotary compressor with high efficiency.

[0002]

2. Description of the Related Art As a general rotary compressor, for example, one disclosed in JP-A-58-44290 is known. This conventional compressor will be described with reference to FIG.

FIG. 10 is a vertical sectional view of a conventional rotary compressor.

In the rotary compressor shown in FIG. 10, the electric motor 6 is arranged in the upper part and the pump part 7 is arranged in the lower part in the hermetic container 1, and the main bearing 2 is provided with the screw hole 8 for fixing the bolt. Bolt fixing through holes 8b are provided in the cylinder 3 and the auxiliary bearing 4 and the discharge muffler 9 at positions opposite to the fixing screw holes 8, respectively, and the bolts 5 are collectively bolted and fixed to the main bearing 2 from the side opposite to the electric motor. It is characterized by.

However, in general, in the case of a compressor of this type, since the main bearing 2, the cylinder 3 and the auxiliary bearing 4 are fastened with the bolts 5 that penetrate therethrough, there is an advantage that they can be manufactured in a small number of steps, but the cylinder is in the rotational axis direction. In the case of a large compressor having a very long length, it is fixed with a long bolt 5 and there is a risk of lateral slippage, so that it has been used in a relatively small rotary compressor for a refrigerator or the like.

In the case of a large compressor, Japanese Patent Laid-Open No. 58-131
It has a structure like the rotary compressor described in Japanese Patent No. 392.

FIG. 11 is a vertical sectional view of the rotary compressor. Further, FIG. 12 is an enlarged sectional view showing a fixed portion of the pump. In FIGS. 11 and 12, the same reference numerals as those in FIG. 10 indicate equivalent components, and detailed description of the configuration will be omitted.

In the rotary compressor shown in FIG. 11, a closed container 1 is formed by pressing and welding a lid chamber 10 and a bottom chamber 11 into a closed container. The outer shape of the stator 6a of the electric motor 6 is joined to the inner diameter of the closed container 1 by shrinkage fitting, and the stator 6a and the rotor 12 of the electric motor 6 are arranged at an appropriate gap. The pump portion 7 is joined to the rotor 12 by press fitting, shrink fitting, etc.
3, a roller 14 fitted and slid on the eccentric portion 13a of the rotor 12, a main bearing 2 which covers sliding of the upper surface of the roller 14 and the upper journal 13b of the rotary shaft 13, and a lower surface of the roller 14. The lower bearing 13c of the rotating shaft 13 and the like, which are covered by sliding, a sub-bearing 4, a main bearing 2, and a sub-bearing 4 are joined together, and are constituted by a cylinder 3 and the like that slidably holds a vane 15 sliding with the outer diameter of the roller Has been done. FIG. 12 shows the main bearing 2,
This shows a state in which the sub bearing 4 and the cylinder 3 are joined. A bolt fixing screw hole 8 is opened in the cylinder 3 and the sub bearing 4, the main bearing 2 and the like are fastened from above and below by bolts 5 as shown in FIG. It is composed. Therefore, since the main bearing 2 and the cylinder 3, and the sub bearing 4 and the cylinder 3 are fastened with separate bolts 5, the number of assembling steps is increased, but the main bearing 2 and the cylinder 3, and the sub bearing 4 and the cylinder 3 are securely connected. Can be fixed.

[0009]

Generally, the tightening torque of a bolt is determined in consideration of the tensile strength of the bolt, shear fracture of the screw thread, prevention of lateral displacement of the object to be fastened, and the like.
Since the bolts are usually made of hardened steel and have sufficient strength, it is the current situation that they are fastened with sufficient torque so that the objects to be fastened do not slip during assembly or operation of the compressor. Therefore, even in the latter prior art, the main bearing and the cylinder, and the sub bearing and the cylinder are fastened with separate bolts, but both are fastened with sufficient torque of the same value to prevent lateral displacement of the fastened object. There is. It is needless to say that since the former conventional technique is fastened with a single through bolt, the tightening torque is the same.

However, it has been confirmed that even when tightened with a torque that does not damage the bolts and threads, the plane portions of the main bearing and the sub bearing and the inner diameter portion of the cylinder are deformed as shown in FIGS. Note that FIG. 3 shows the circularity of the inner diameter of the cylinder 3 before and after tightening the bolts, and shows the deformed state after tightening (solid line display B) in comparison with before tightening (dotted line display A). Is. In addition, 8a shows a bolt hole position. As shown in FIG. 3, it can be seen that the cylinder 3 inner diameter circularity after tightening the bolt is deformed inward in the vicinity of the bolt as compared with the cylinder 3 inner diameter circularity before tightening. FIG. 4 shows the flatness of the main bearing 2 and the auxiliary bearing 4 before and after tightening the bolts, and shows the deformation state after tightening (solid line C) compared to before tightening (dotted line D). It is shown. In FIG. 4, 8a corresponds to FIG.
The bolt holes are shown in the same manner as. As shown in FIG. 4, the flatness of each of the end faces of the main bearing 2 and the sub bearing 4 contacting the cylinder after bolt tightening rises toward the cylinder end face near the bolt, and at the center end face between the bolts, It can be seen that the cylinder deforms so as to dent in the direction opposite to the cylinder end surface side. In addition, the main bearing 2, the cylinder 3, the sub bearing 4
It was found that the deformation was large near the contact part of. When the deformation inside the pump is large, the clearances in the rotation axis direction and the radial direction with the roller of the rolling piston that eccentrically rotates inside the pump due to the rotation of the rotation shaft are not uniform. Therefore, in the conventional compressor, oil leakage (including the refrigerant) into the cylinder increases due to the non-uniformity of the clearance, and sliding loss increases due to metal contact between the inside of the pump and the roller. There was a problem of reduced efficiency. The present invention has been made to solve the above-mentioned problems of the prior art, and an object thereof is to provide a highly efficient rotary compressor by minimizing the deformation inside the pump after the compressor is assembled. Especially.

[0011]

In order to achieve the above object, the structure of a rotary compressor according to the present invention comprises an electric motor part and a compression mechanism part in a hermetically sealed container to rotate the rotational force of the electric motor. In a rotary compressor that is transmitted to a compression mechanism section by a shaft and compresses a refrigerant gas in the compression mechanism section, the compression mechanism section is obtained by superposing respective elements of a main bearing, a cylinder, and a sub bearing from the electric motor side. The cylinder is fixed to the closed container by welding or the like, the main bearing is fastened to the cylinder with a bolt, and the auxiliary bearing is fastened to the cylinder with a torque weaker than the fastening force of the bolt by 10 kgf · cm or more. did.

Further, according to another means of the present invention, the compression mechanism portion is constituted by superposing the respective elements of the main bearing, the cylinder and the sub bearing, and the main bearing and the sub bearing are fastened to the cylinder by separate bolts. In the above rotary compressor, the fastening internal thread portion processed into the cylinder has a guide hole, and the guide hole has a diameter not less than the root diameter of the internal thread and a depth not less than 2 mm. .

Further, in order to further reduce the deformation inside the pump, the compression mechanism portion is constituted by superposing the respective elements of the main bearing, the cylinder and the sub bearing, and the main bearing and the sub bearing are respectively cylinders with separate bolts. In the rotary compressor fastened to the above, a discharge valve is formed in the sub bearing, the sub bearing is fastened with a torque of 10 kgf · cm or more weaker than the main bearing, and the fastening female screw portion machined in the cylinder is guided. The guide hole has a diameter of not less than the root diameter of the female screw and a depth of not less than 2 mm.

Regarding the tightening torque, specifically, four M6 bolts are used on each of the main bearing side and the sub bearing side, and the main bearing side is tightened at 80 to 100 kgf · cm.
The sub bearing side is tightened at 70 to 90 kgf · cm.

When four M5 bolts are used, the main bearing side is tightened at 65 to 85 kgf · cm, and the sub bearing side is tightened at 55 to 75 kgf · cm.

Further, when four M4 bolts are used, the main bearing side is tightened at 50 to 70 kgf · cm, and the sub bearing side is tightened at 40 to 60 kgf · cm.

Furthermore, when six M6 bolts are used, the main bearing side is tightened at 70 to 90 kgf · cm, and the sub bearing side is tightened at 60 to 80 kgf · cm.

Further, when six M5 bolts are used, the main bearing side is tightened at 55 to 75 kgf · cm and the sub bearing side is tightened at 45 to 65 kgf · cm.

When six M4 bolts are used, the main bearing side is tightened at 40 to 60 kgf · cm and the sub bearing side is tightened at 30 to 50 kgf · cm.

[0020]

During operation, a gas compression load acts on the eccentric portion of the rotary shaft inside the pump, and a magnetic attraction force acts on the rotor of the electric motor unit fixed to the rotary shaft by shrink fitting or the like.
Here, with respect to the former gas compression load, it acts in a distributed manner on the main bearing and the auxiliary bearing that support the rotating shaft, but regarding the latter magnetic attraction force, the crankshaft tilts in the main bearing and the upper end of the main bearing Since the load acts on the lower part and the lower part, the total load in the radial direction, that is, the lateral displacement load, is larger between the main bearing and the cylinder than between the sub bearing and the cylinder.

Therefore, the minimum tightening torque for preventing lateral deviation can be set smaller on the auxiliary bearing side than on the main bearing side.

Further, as a result of the measurement, when tightened with the same torque, the flatness of the end face of the bearing becomes worse when the discharge valve is installed. Therefore, the minimum tightening torque can be set smaller than that of the main bearing. By installing the discharge valve on the side, deformation inside the pump can be reduced.

Further, FIG. 6 shows a deformed state in the pump when the guide hole 16 is installed in the end surface portion of the cylinder 3. When the guide hole 16 is provided, it is possible to improve the roundness in the vicinity of the end portion of the wall surface of the cylinder 3 as compared with the conventional case of FIG. This is because when the cylinder 3 is compressed in the axial direction and expanded and deformed in the radial direction, the deformation in the inner diameter direction of the cylinder 16 is suppressed by the amount of the clearance provided in the guide hole 16. Since the deformation particularly concentrates near the end portion of the cylinder 3, if the guide hole 16 is formed with a depth of 2 mm or more, the roundness of the inner wall surface of the cylinder 3 is significantly improved. Further, FIG. 5E is a conventional cylinder inner diameter circularity deformation amount, FIG. 6F is a guide cylinder inner diameter circularity deformation amount, and FIG. 6G is a guide inner diameter circularity deformation amount enlarged at the same ratio. Is.

When the present invention relating to the tightening torque of the bolt 5 and the present invention in which the guide hole 16 is installed in the cylinder 3 are used in combination, the flatness of the end faces of the main bearing 2 and the sub bearing 4 and the true inner wall surface of the cylinder 3 are used. Since both the circularity can be improved, the clearance between the roller eccentrically rotating inside the pump and the inside of the pump in the rotational axis direction and the radial direction becomes more uniform, and the oil leakage (including the refrigerant) into the cylinder 3 is reduced. When,
The efficiency of the compressor is further improved by reducing sliding loss due to metal contact between the inside of the pump and the roller.

[0025]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to FIGS.

FIG. 1 is a vertical sectional view of a rotary compressor according to an embodiment of the present invention. 2 is a sectional view taken along the line GG in FIG. In FIG. 1, an electric motor 6 including a stator 6a and a rotor 12, a rotary shaft 13, a cylinder 3, a main bearing 2, a sub bearing 4, a roller 14, a vane 15, and a spring 17 are provided in a closed container 1 which also functions as an oil sump. And a pump unit 7 including the same. In the electric motor 6, the stator 6a is fixed in the closed container 1 by shrink fitting. The rotor 13 has one end fixed to the rotor 12 and the other end supported by the main bearing 2 and the sub bearing 4. The main bearing 2 and the sub bearing 4 also serve as side plates of the cylinder 3, and are arranged on both sides of the cylinder 3 to form a cylinder chamber 3a. Here, the cylinder 3 is fixed in the closed container 1 by welding or the like, and the main bearing 2 and the sub bearing 4
Are fastened to the cylinder 3 from both sides by separate bolts, respectively, to form the pump unit 7 and the rotary shaft 13
Is to support. Further, the cylinder 3 is provided with a groove 18 as shown in FIG. 2, and in the groove 18,
The vane 15 is fitted. One end of the vane 15 is in contact with the roller 14 inserted into the eccentric portion 13 a of the rotary shaft 13, and the other end is pressed by the spring 17. In the rotary compressor configured as described above, the rotor 12 rotates when the electric element 6 is energized, and the rotation is transmitted to the pump unit 7 by the rotary shaft 13 directly connected to the rotor 12. The roller 1 inserted into the rotary shaft 13 by the transmitted rotary motion.
4 is eccentric along the inner diameter of the cylinder 3. This roller 1
The rotation of vane 15 and the rotation of vane 15 cause cylinder 3 to move as shown in FIG.
A low pressure chamber 19 and a high pressure chamber 20 are formed as shown in FIG. The low-pressure chamber 19 is moved to the high-pressure chamber 20 by the eccentric movement of the roller 14, and the compression operation is performed. Further, the main bearing 2 and the sub bearing 4 are respectively fastened to the cylinder 3 by separate bolts 5, and the female thread portion for fastening which is processed on the cylinder 3 has a guide hole 16, and the guide hole 16 has a diameter of The depth is 2 mm or more at the root diameter of the female thread or more. Further, the number of bolts 5 for fixing the main bearing 2 and the sub bearing 4 is M6, and four bolts 5 each. The tightening torque for tightening is 80 to 100 kg on the main bearing 2 side.
f ・ cm, the sub bearing 4 side is 70 to 90 kgf ・ cm,
On average, the main bearing 2 is tighter than the sub bearing 4 by 10 or more.

The effect of the portion relating to the bolt tightening torque in this embodiment will be described. The main bearing 2 is fastened to the cylinder 3 with bolts 5, and the sub bearing 4 is fastened to the cylinder 3 with a torque weaker than the fastening force of the bolts by 10 kgf · cm or more, whereby the flatness of the end faces of the main bearing 2 and the sub bearing 4 is increased. Since both the circularity of the inner wall surface of the cylinder 3 and the roundness of the inner wall surface of the cylinder 3 can be improved, the clearance between the roller 14 that eccentrically rotates inside the pump and the inside of the pump becomes even more uniform in the rotation axis direction and the radial direction, and the oil leakage ( The efficiency of the compressor is further improved by reducing the amount of the refrigerant (including the refrigerant) and the sliding loss due to the metal contact between the inside of the pump and the roller 14.

Next, a detailed description of the bolt fastening of this embodiment will be given with reference to FIGS. In FIG. 7, the horizontal axis represents the tightening torque T, the vertical axis represents the main bearing and the sub-bearing end surface flatness deformation coefficient n, H represents the sub-bearing end surface deformation characteristic, and I represents the main bearing end surface deformation characteristic. Main bearing, sub bearing end face flatness deformation coefficient n
Is expressed as (end face flatness after tightening on main / sub bearing side) / (end face flatness before tightening on main / sub bearing side) × 100,
The figure shows the case where four main bearings, sub bearings, and four M6 bolts are used. As can be seen from FIG. 7, when the tightening torque T is 100 kgf · cm or more, the main bearing / sub bearing end face flatness deformation coefficient n sharply increases. Here, the reason why the flatness of the auxiliary bearing is poorer than that of the main bearing is that the discharge valve is installed on the auxiliary bearing. This is due to the phenomenon that the thickness of the flange portion becomes thin at the valve installation portion, so that the deformation becomes large.
In this embodiment, the main bearing side is tightened at 80 to 100 kgf · cm, and the sub bearing side is tightened at 70 to 90 kgf · cm, so that the main bearing / sub bearing end face flatness deformation coefficient n is 300 at maximum. Generally, in the case of M6 bolts, since it is tightened at 110 kgf · cm or more, the flatness deformation coefficient n of the end surface of the main bearing and the sub-bearing reaches 440 or more in the sub-bearing. The degree improves.

Next, in FIG. 8, the horizontal axis represents the tightening torque T, the vertical axis represents the cylinder inner diameter roundness deformation coefficient m, and J represents the main and auxiliary bearing side cylinder inner diameter deformation characteristics. The cylinder inner diameter circularity deformation coefficient m here is represented by (cylinder circularity after tightening the main and auxiliary bearings) / (cylinder circularity before tightening the main and auxiliary bearings) .times.100. The bolt is M6
Are fastened to the cylinder with four main bearings and four sub bearings. Regarding the roundness of the cylinder, the same deformation occurs on the main bearing side and the sub bearing side. Further, this modification is data on a portion 1 mm from the end surface of the cylinder. As can be seen from FIG. 8, as the tightening torque T becomes 100 kgf · cm or more, the cylinder inner diameter circularity deformation coefficient m of the main bearing side and the sub bearing side rapidly increases. In this embodiment, as described above, the main bearing side is tightened at 80 to 100 kgf · cm,
Since the auxiliary bearing side is tightened at 70 to 90 kgf · cm, the cylinder inner diameter circularity deformation coefficient m of the main bearing and the auxiliary bearing side is 300 at maximum. In case of general M6 bolt, 110
The cylinder inner diameter circularity deformation coefficient m of the main bearing and the sub-bearing side clamped at kgf · cm or more is 400, which is a 25% improvement in circularity as compared with the above embodiment. On the other hand, a description will be given below regarding the lateral shift force and the axial fastening force applied to the fastening surface between the main bearing and the cylinder and the fastening surface between the auxiliary bearing and the cylinder during operation. In the compressor described in this embodiment, the magnetic attraction force applied to the center of the rotor during operation is about 52 kgf, and the gas compression load applied to the eccentric portion of the rotating shaft is about 140 kgf. Since the rotating shaft on which the magnetic attraction acts is supported near the lower end of the main bearing which is the same as near the upper end of the main bearing, the difference 52 kgf between the upper end and the lower end acts on the main bearing in the direction orthogonal to the shaft. . Moreover, the gas compression load acts on both the main bearing and the sub bearing, and 55 kgf on the main bearing side and 85 kgf on the sub bearing side.
To work. Therefore, a total of 107 kgf is applied to the main bearing and 85 kgf is applied to the auxiliary bearing, and a large amount of lateral displacement load acts on the main bearing side. On the other hand, the lower limit of the tightening torque in this embodiment is 80 kgf · cm for the main bearing and 70 kgf · cm for the auxiliary bearing, and when the tightening force in the axial direction is calculated, the total of four bolts is 2420 kgf on the main bearing side and the auxiliary bearing. The bearing side weighs 2120 kgf. Main bearing,
Assuming that the friction coefficient of the tightening surface between the cylinder, the sub bearing and the cylinder is 0.1, the limit lateral slip load is 24 on the main bearing side.
It is 2 kgf and 212 kgf on the sub bearing side, and it can be said that a safety factor (limit lateral deviation load ÷ lateral deviation load) of 2 or more can be secured for both the main and auxiliary bearings. Also, as a result of the experiment, it was confirmed that it was tightened with a necessary and sufficient torque against impact.

While the above description has described the effect of the portion relating to the optimum tightening torque, the portion relating to the guide hole installed in the female thread portion of the cylinder will be described next.

In the rotary compressor in which the compression mechanism portion is formed by superposing the respective elements of the main bearing, the cylinder and the auxiliary bearing, and the main bearing and the auxiliary bearing are fastened to the cylinder by separate bolts, The machined fastening female screw portion has a guide hole, and the guide hole has a diameter not less than the root diameter of the female screw and a depth not less than 2 mm to improve the roundness of the inner wall surface of the cylinder. effective. This is because when the cylinder is compressed in the axial direction and expanded and deformed in the radial direction, the deformation in the inner diameter direction of the cylinder is suppressed by the amount of the clearance provided in the guide hole. Since the deformation is concentrated especially near the end portion of the cylinder, if the guide hole is formed with a depth of 2 mm or more, the roundness of the inner wall surface of the cylinder is significantly improved.

Next, the effect of installing the guide hole will be described with reference to FIG. In FIG. 9, the horizontal axis represents the tightening torque T, the vertical axis represents the cylinder inner diameter roundness deformation coefficient m, and J
Is a guide hole with no guide hole Main and sub bearing side cylinder bore deformation characteristics, K
Shows the deformation characteristics of the main and auxiliary bearing side cylinders with guide holes. Here, in this embodiment, the main bearing side is 80 to 100
Since it is tightened with kgf · cm and the auxiliary bearing is tightened with 70 to 90 kgf · cm, the cylinder inner diameter circularity deformation coefficient m of the main and auxiliary bearings when the guide holes are installed in each bolt hole of the cylinder is the maximum. When the tightening torque is 250, the main and auxiliary bearing side cylinder inner diameter circularity deformation coefficient m is 300 at the maximum, and the guide hole improves the circularity by 17%. In the case of general M6 bolt, 1
Since it is tightened at 10 kgf · cm or more and no guide hole is installed, the cylinder inner diameter circularity deformation coefficient m of the main and auxiliary bearings is 400. Compared with m250, the roundness is improved by 37% with the guide hole.

Next, another embodiment will be described.

In the pump part, four M5 bolts are used for fixing the main bearing and cylinder and for fixing the sub bearing and cylinder, and 65 to 85 kg on the main bearing side by these bolts.
Even when tightened at f · cm and at the auxiliary bearing side at 55 to 75 kgf · cm, the same effect as in the above-described embodiment can be obtained. This is because when the bolt is reduced from M6 to M5,
This is because the torque for obtaining the tightening force acting in the axial direction of the bolt becomes small. At the final tightening torque,
As a result of the experiment, it was confirmed that the main and sub bearing end surface flatness deformation coefficient n and the main and sub bearing side cylinder inner diameter circularity deformation coefficient m are the same as in the case of M6.

As a result of repeating the same experiment, it was found that the necessary and sufficient types of bolts, the number of bolts, and the torque for achieving the same deformation have the following relationships.

4 main bearings and 4 sub bearings with bolts M4
The torque when tightened with a book is 50 to 70 on the main bearing side.
kgf ・ cm, 40-60kgf ・ cm on the secondary bearing side.

The main bearing and the sub bearing are 6 each with a bolt M6.
The torque when tightened with a book is 70 to 90 on the main bearing side.
kgf · cm, 60 to 80 kgf · cm on the secondary bearing side.

The main bearing and the sub bearing are each 6 with the bolt M5.
The torque when tightened with a book is 55 to 75 on the main bearing side.
kgf · cm, the auxiliary bearing side is 45 to 65 kgf · cm.

The main bearing and the sub bearing are each 6 with the bolt M4.
The torque when tightened with a book is 40 to 60 on the main bearing side.
kgf · cm, 30 to 50 kgf · cm on the secondary bearing side.

The invention relating to the above tightening torque has some effects even when it is used separately from the invention in which a guide hole is provided in a tightening bolt hole formed in a cylinder, but it is used at the same time. In this case, as described above, the flatness of the end faces of the main bearing and the sub bearing and the roundness of the cylinder inner diameter are further improved.

As a result of mounting the rotary compressor described above in a room air conditioner for home use, it has been found that the power consumption can be reduced by about 5% compared to the past. It was also found that as a result of mounting the rotary compressor described above in a household refrigerator, power consumption can be reduced to almost the same level as that in the room air conditioner.

In the above embodiment, the vertical type rotary compressor has been described, but the same effect can be obtained even in the horizontal type.

[0043]

As described in detail above, according to the present invention, it is possible to reduce the tightening deformation when fixing the main bearing, the cylinder, and the sub bearing with bolts, so that a highly efficient rotary compressor is provided. can do.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view of a sliding portion of a rotary compressor according to an embodiment of the present invention.

FIG. 3 is a schematic diagram showing deformation of a cylinder inner diameter circularity of a rotary compressor according to an embodiment of the present invention.

FIG. 4 is a main part of a rotary compressor according to an embodiment of the present invention,
It is a schematic diagram which showed the deformation | transformation of a sub bearing end surface flatness.

5A and 5B are a schematic view showing deformation of a circularity of a cylinder inner diameter of a conventional rotary compressor, and a cross-sectional view near a bolt hole.

6A and 6B are a schematic view showing deformation of a cylinder inner diameter roundness of a rotary compressor according to an embodiment of the present invention, and a sectional view of a portion near a bolt hole.

FIG. 7 is a graph showing main and sub bearing end face flatness deformation characteristics in which the vertical axis represents a main and sub bearing end surface flatness deformation coefficient and the vertical axis represents a tightening torque in a rotary compressor according to an embodiment of the present invention. Is.

FIG. 8 shows main and auxiliary bearing side cylinder inner diameter circularity deformation characteristics in which the vertical axis represents a cylinder inner diameter circularity deformation coefficient and the vertical axis represents a tightening torque in a rotary compressor according to an embodiment of the present invention. It is a graph.

FIG. 9 is a rotary compressor according to an embodiment of the present invention, in which the vertical axis represents the cylinder inner diameter circularity deformation coefficient and the vertical axis represents the tightening torque, the guide holeless main and auxiliary bearing side cylinder inner diameter circularity deformations. 5 is a graph showing characteristics and characteristics of main and auxiliary bearing side cylinder bore circularity deformation characteristics with guide holes.

FIG. 10 is a sectional view of a sliding portion of a rotary compressor, which is one of conventional rotary compressors.

FIG. 11 is a cross-sectional view of a rotary compressor that is one of conventional rotary compressors.

FIG. 12 is a sectional view of a sliding portion of a rotary compressor, which is one of conventional rotary compressors.

[Explanation of symbols]

 1 ... Airtight container, 2 ... Main bearing, 3 ... Cylinder, 4 ... Sub bearing, 5 ... Bolt, 6 ... Electric motor, 6a ... Stator, 7 ... Pump part, 8 ... Bolt hole, 8a ... Bolt hole position, 8b ... Through holes for fixing bolts, 9 ... Discharge muffler, 10 ... Lid chamber, 11 ... Bottom chamber, 12 ... Rotor, 13 ... Rotating shaft, 13a ... Eccentric part, 13b ... Upper journal part, 13c ... Lower journal part, 14 ... Roller, 15 ... Vane, 16 ... Guide hole, 17 ... Spring, 18 ... Groove, 19 ... Low pressure chamber, 20 ... High pressure chamber.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mikiko Tanaka 800, Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture Hitachi Ltd. Living Equipment Division

Claims (10)

[Claims] 1. A rotary compressor in which a hermetically sealed container is provided with an electric motor section and a compression mechanism section, the rotational force of the electric motor is transmitted to the compression mechanism section by a crankshaft, and the refrigerant gas is compressed by the compression mechanism section. The compression mechanism section is formed by superposing each element of a main bearing, a cylinder, and a sub bearing from the electric motor side, and the cylinder is fixed to a closed container by welding or the like, and the main bearing is fixed to the cylinder by a bolt. The rotary compressor, wherein the auxiliary bearing is fastened to the cylinder with a torque that is 10 kgf · cm or more weaker than the fastening force of the bolt. 2. A rotary compressor in which a compression mechanism portion is formed by superposing respective elements of a main bearing, a cylinder, and a sub bearing, and the main bearing and the sub bearing are fastened to the cylinder by separate bolts, respectively. A rotary compressor characterized in that a female thread portion for fastening which is processed into a cylinder has a guide hole, and the guide hole has a diameter not less than a root diameter of the female thread and a depth not less than 2 mm. 3. A rotary compressor in which a compression mechanism section is formed by superposing respective elements of a main bearing, a cylinder, and a sub-bearing, and the main bearing and the sub-bearing are respectively fastened to the cylinder by separate bolts. The discharge valve is formed in the bearing, the auxiliary bearing is fastened with a torque weaker than 10 kgf · cm than the main bearing, and the female thread portion for fastening processed on the cylinder has a guide hole. 3. The rotary compressor according to claim 1, wherein the diameter is equal to or larger than the root diameter of the female screw and the depth is equal to or larger than 2 mm. 4. The compression mechanism section is composed of a main bearing, a cylinder, a sub bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the sub bearing and the cylinder.
There are four M6 on each sub-bearing side. Tighten at 80 to 100 kgf · cm on the main bearing side, and 70 to 90 kgf ·· on the sub-bearing side.
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened in cm. 5. A compression mechanism portion is composed of a main bearing, a cylinder, a sub bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the sub bearing and the cylinder, and the bolt is used for the main bearing side.
There are four M5 on each sub-bearing side, tightening at 65 to 85 kgf · cm on the main bearing side, and 55 to 75 kgf · cm on the sub-bearing side.
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened with. 6. A compression mechanism portion is composed of a main bearing, a cylinder, a sub bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the sub bearing and the cylinder.
There are 4 M4 each on the sub bearing side. Tighten 50 to 70 kgf · cm on the main bearing side and 40 to 60 kgf · cm on the sub bearing side.
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened with. 7. A compression mechanism portion is composed of a main bearing, a cylinder, an auxiliary bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the auxiliary bearing and the cylinder, and the bolt is used for the main bearing side,
The secondary bearing side has 6 M6 each, the main bearing side is tightened at 70 to 90 kgf · cm, and the secondary bearing side is 60 to 80 kgf · cm.
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened with. 8. A compression mechanism portion is composed of a main bearing, a cylinder, a sub bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the sub bearing and the cylinder, and the bolt is used for the main bearing side,
Six M5 on each sub-bearing side, tightening at 55 to 75 kgf · cm on the main bearing side, 45 to 65 kgf · cm on the sub-bearing side
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened with. 9. A compression mechanism portion is composed of a main bearing, a cylinder, a sub bearing, etc., and bolts are used for fixing the main bearing and the cylinder and for fixing the sub bearing and the cylinder.
The auxiliary bearing side has 6 M4 each, the main bearing side is tightened at 40 to 60 kgf · cm, and the auxiliary bearing side is 30 to 50 kgf · cm.
The rotary compressor according to claim 1 or 3, wherein the rotary compressor is tightened with. 10. An air conditioner equipped with the rotary compressor according to any one of claims 1 to 9.