JP4420040B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor used in a refrigerant circuit for a refrigeration air conditioner.

Conventionally, this type of compressor, for example, a rotary compressor, is configured as shown in FIG.
FIG. 3 is a diagram showing the structure of a conventional compressor disclosed in, for example, Japanese Utility Model Laid-Open No. 62-152094 and Japanese Patent Laid-Open No. 61-93292.
In the figure, 1 has an electric element 2 and a compression element 3 which will be described later, and a sealed container in which lubricating oil (not shown) for lubricating the compression element 3 is sealed at the bottom, 2 is a crankshaft 5 which will be described later. Is an electric element having an electric motor rotor 2a that is firmly inserted into a rotor insertion portion (not shown) and rotates the crankshaft 5. Reference numeral 3 denotes a cylinder 4, a crankshaft 5, a rolling piston 6, a long bearing 7, The compression element is composed of a bearing 8 and is driven by the driving force as the rotational force of the electric element 2 to compress the refrigerant gas, 4 is a cylinder that compresses the refrigerant gas by the rotation of the rolling piston 6, and 5 is processed coaxially. A long shaft 5a, a short shaft 5b, and an eccentric shaft 5c sandwiched between them and having an eccentric shaft center parallel to them, and can rotate to a long bearing 7 and a short bearing 8 as bearings described later. The crankshaft 6 is inserted into and rotated by the driving force of the electric element 2, 6 is a rolling piston that is inserted into the eccentric shaft 5 c of the crankshaft 5 and rotates together with the crankshaft 5, and 7 is the long shaft 5 a of the crankshaft 5. A long bearing 8 is rotatably inserted, and 8 is a short bearing in which the short shaft 5b of the crankshaft 5 is rotatably inserted. The long bearing 7 and the short bearing 8 constitute a pair of upper and lower bearings.

Reference numeral 9 denotes an opening in one end of the short shaft 5b of the crankshaft 5, and a vertical hole drilled along the longitudinal direction. Reference numeral 10 denotes a long bearing 7 in the long shaft 5a, the short shaft 5b, and the eccentric shaft 5c. A plurality of oil supply lateral holes 11, which are drilled so as to communicate with the bearing 8 and the cylinder 4, extend from the vertical hole 9 of the crankshaft 5 toward the outer diameter of the long axis 5 a and into the sealed container 1. It is a side hole for venting gas communicating.
The crankshaft 5 serves to transmit the driving force of the electric element 2 to the compression element 3.
The rotor insertion portion and the long bearing 7 have substantially the same diameter.

Next, the operation will be described.
First, the crankshaft 5 is rotated by the electric element 2.
Next, the rotation of the crankshaft 5 rotates the rolling piston 6 into which the eccentric shaft 5 c of the crankshaft 5 is inserted, and the refrigerant gas is compressed in the cylinder 4.

  At this time, the lubricating oil sealed in the bottom of the hermetic container 1 rises in the vertical hole 9 in the crankshaft 5 by the water head accompanying the rotation generated in the vertical hole 9 of the crankshaft 5, and the long shaft 5a and the short shaft 5b. The long bearing 7, the short bearing 8 and the inner diameter of the rolling piston 6 are supplied from the oil supply lateral holes 10 respectively connected to the eccentric shaft 5c.

  In order to smoothly supply the oil, it is necessary to prevent the refrigerant gas mixed in the lubricating oil from staying in the vertical hole 9, and thus it is necessary to discharge the gas from the vertical hole 9. In this conventional example, a degassing lateral hole 11 is provided in the outer diameter direction of the long shaft 5 a for degassing from the vertical hole 9 into the sealed container 1, and forced by utilizing the centrifugal force associated with the rotation of the crankshaft 5. The method of exhausting gas is taken.

  However, in the conventional rotary compressor, as described above, the degassing lateral hole 11 opens in the finished surface of the long shaft 5a. Further, the side hole 11 for venting has the same or larger area as the side hole 10 for refueling so that gas can escape efficiently. Therefore, in grinding finishing of the crankshaft 5, excessive grinding, which has been negligible because the diameter of the lateral hole 10 for oiling is small in the vicinity of the lateral hole 10 for oiling, cannot be ignored in the vicinity of the lateral hole 11 for venting gas. . That is, in the vicinity of the degassing horizontal hole 11, since the diameter of the degassing horizontal hole 11 is large, the polishing surface pressure is higher than the others, and grinding tends to occur excessively and the roundness tends to deteriorate. It was. Therefore, in order to ensure the roundness of the crankshaft 5, there has been a problem that mass productivity is lowered, such as devising the operation of a grindstone.

FIG. 4A is an enlarged view schematically showing a state where roundness is deteriorated due to excessive grinding only in the vicinity of the degassing lateral hole 11 in the long axis 5a of the crankshaft 5, FIG. 4B. These are the fragmentary sectional views of the long axis 5a of the crankshaft 5 of Fig.4 (a). In the figure, 5f is a roundness deterioration region where the roundness has deteriorated.
When the roundness deteriorates as shown in FIG. 4, for example, the position of the cross section indicated by DD in the drawing, that is, the cross section of the roundness deterioration region 5 f falls within the region of the long bearing 7. Remarkably lowering, it becomes a factor of lowering reliability.

  As another conventional example, FIG. 5 shows the structure of a rotary compressor as shown in, for example, Japanese Utility Model Laid-Open No. 58-156183. In this example, there is no horizontal hole 11 for degassing, and the vertical hole 9 communicates with the upper part of the sealed container 1 as it is. In such a structure, the roundness at the time of finishing the crankshaft 5 described above does not deteriorate, but forced gas discharge due to centrifugal force expected when the side hole 11 for degassing is provided is expected. As a result, gas could not be discharged from the inside of the vertical hole 9 and the oil supply capability for the long shaft 5a, the short shaft 5b, and the eccentric shaft 5c could be lowered.

  FIG. 6 is a structural view of the vicinity of the oil supply lateral hole 10 opened on the long axis 5a of the crankshaft 5 of the hermetic electric compressor disclosed in Japanese Patent Laid-Open No. 55-19922. The lateral hole 10 for refueling also has a function of discharging gas.

In this example, the radius is configured to be smaller than the long shaft 5 a of the crankshaft 5 in the vicinity of the lateral hole 10 for refueling, and when the long shaft 7 is inserted into the long shaft 7, an annular shape is formed between the long shaft 5 a and the long shaft 7. Region 12 is formed.
In this way, the annular region 12 is formed, and the oil supply lateral hole 10 is opened in the annular region 12, so that the gas and lubricating oil discharged from the oil supply lateral hole 10 once enter the annular region 12. In the annular region 12, the gas moves upward and the lubricating oil moves downward due to the specific gravity difference between the gas and the lubricating oil. The gas that has moved upward is released into the sealed container 1 through the gap between the long bearing 7 and the long axis 5a of the crankshaft 5. On the other hand, the lubricating oil that has moved downward is supplied between the long bearing 7 and the crankshaft 5.
However, since the lateral hole 10 for refueling opens into the annular region 12, forced gas discharge due to centrifugal force cannot be expected. Accordingly, the ability to discharge gas is inferior to that of the conventional example of FIG. 3 in which the degassing lateral hole 11 is directly communicated with the sealed container 1, and as a result, the ability to supply oil to the long shaft 5a, the short shaft 5b, and the eccentric shaft 5c is also reduced. descend.

  The present invention has been made to solve the above-described problems, and employs a method of forcibly discharging gas by utilizing centrifugal force accompanying rotation of the crankshaft 5 and finishing the crankshaft 5. It aims at providing the compressor which can prevent the deterioration of the roundness at the time of processing.

  A compressor having an electric element, a compression element that is driven by a driving force of the electric element, and a shaft that is rotatably inserted into a bearing and that transmits the driving force of the electric element to the compression element. The shaft has an opening at one end and a hole drilled along the longitudinal direction, an annular relief region having a diameter different from the diameter of the portion contacting the bearing, an opening in the relief region, and a relief region from the hole And the relief area is not fitted into the bearing.

  Further, the shaft is provided with an oil supply hole which is drilled so as to communicate with the bearing in a place contacting the bearing, and the area of the communication hole is equal to or larger than the area of the oil supply hole. is there.

  A compressor having an electric element, a compression element that is driven by a driving force of the electric element, and a shaft that is rotatably inserted into a bearing and that transmits the driving force of the electric element to the compression element. The shaft has an opening at one end and a hole drilled along the longitudinal direction, an annular relief region having a diameter different from the diameter of the portion contacting the bearing, an opening in the relief region, and a relief region from the hole Since the relief area is not inserted into the bearing, the long shaft has a uniform polishing area over the entire circumference and can be processed with good roundness. .

  Further, the shaft is provided with an oil supply hole which is drilled so as to communicate with the bearing in a place contacting the bearing, and the area of the communication hole is equal to or larger than the area of the oil supply hole. Therefore, it is possible to avoid a decrease in the function of releasing the gas in the degassing horizontal hole due to factors such as adhesion of lubricating oil to the degassing horizontal hole.

Embodiment 1 FIG.
FIG. 1 is a sectional view showing the structure of a rotary compressor according to this embodiment of the present invention, FIG. 2 (a) is an enlarged view of a crankshaft 5 in FIG. 1, and FIG. 2 (b) is a crank in FIG. 3 is a partial cross-sectional view of a long axis 5a of a shaft 5. FIG.
In the figure, 1 has an electric element 2 and a compression element 3 which will be described later, and a sealed container in which lubricating oil (not shown) for lubricating the compression element 3 is sealed at the bottom, 2 is a crankshaft 5 which will be described later. Is an electric element having an electric motor rotor 2a that is firmly inserted into a rotor insertion portion (not shown) and rotates the crankshaft 5. Reference numeral 3 denotes a cylinder 4, a crankshaft 5, a rolling piston 6, a long bearing 7, The compression element is composed of a bearing 8 and is driven by the driving force as the rotational force of the electric element 2 to compress the refrigerant gas, 4 is a cylinder that compresses the refrigerant gas by the rotation of the rolling piston 6, and 5 is processed coaxially. The long shaft 5a, the short shaft 5b, the eccentric shaft 5c sandwiched between them and the shaft center being eccentric in parallel with them, and a part of the long shaft 5a is in contact with the finished surface of the long shaft 5a, that is, the long bearing 7 A crankshaft which has a relief region 5d whose diameter is one step smaller, is rotatably inserted into a long bearing 7 and a short bearing 8 as bearings described later, and is rotated by the driving force of the electric element 2, 6 is a crank A rolling piston that is inserted into the eccentric shaft 5c of the shaft 5 and rotates with the crankshaft 5, a long bearing 7 into which the long shaft 5a of the crankshaft 5 is rotatably inserted, and a short shaft 5b of the crankshaft 5 that rotates. It is a short bearing that is freely inserted, and the long bearing 7 and the short bearing 8 constitute a pair of upper and lower bearings.

  9 is a vertical hole opened at one end of the short shaft 5b, and 10 is a portion in contact with the long bearing 7, short bearing 8 and cylinder 4 from the vertical hole 9 in the long shaft 5a, short shaft 5b and eccentric shaft 5c, respectively. A plurality of oil supply lateral holes 11 pierced so as to communicate with each other up to the outer diameter direction of the long axis 5a from the inside of the vertical hole 9 of the crankshaft 5 at a position where the opening end opens into the escape region 5d. This is a side hole for venting gas communicating with the inside.

The crankshaft 5 serves to transmit the driving force of the electric element 2 to the compression element 3.
When the crankshaft 5 is inserted into the long bearing 7, the relief region 5 d is not inserted into the long bearing 7, that is, protrudes from the upper bearing 7.
The rotor insertion portion and the long bearing 7 have substantially the same diameter.
In addition, the area of the horizontal hole 11 for degassing is characterized by having the same or larger area than any of the plurality of horizontal holes 10 for refueling.

Next, the operation will be described with reference to FIG.
First, the crankshaft 5 is rotated by the electric element 2.
Next, the refrigerant gas is compressed in the cylinder 4 by the rotation of the crankshaft 5, that is, the rolling piston 6.

  At this time, the lubricating oil sealed in the bottom of the hermetic container 1 rises in the vertical hole 9 in the crankshaft 5 by the water head accompanying the rotation generated in the vertical hole 9 of the crankshaft 5, and the long shaft 5a and the short shaft 5b. Then, the oil is supplied to the long bearing 7, the short bearing 8, and the inner diameter portion of the rolling piston 6 from the oil supply lateral holes 10 respectively communicating with the eccentric shaft 5 c.

  Further, the gas that has moved up the vertical hole 9 together with the lubricating oil reaches the top of the vertical hole 9. In the present embodiment, since the degassing horizontal hole 11 is provided in a direction orthogonal to the rotation axis of the crankshaft 5, the gas reaching the top is forced by the centrifugal force generated by the rotation of the crankshaft 5. The gas is discharged into the sealed container 1 through the degassing lateral hole 11.

Next, the configuration of the crankshaft 5 will be described with reference to FIG.
As shown in FIG. 2 (a), the crankshaft 5 has a long shaft 5a, an eccentric shaft 5c, a short shaft 5b, and a relief region in which a part of the long shaft 5a is smaller in diameter than the finished surface of the long shaft 5a. 5d. Further, a degassing horizontal hole 11 is formed in the upper part of the vertical hole 9 so as to communicate from the vertical hole 9 to the escape region 5d.

  FIG. 2B shows a partial cross-sectional view of the long axis 5 a of the crankshaft 5. As described above, since the degassing lateral hole 11 is opened in the escape region 5d, the polishing surface pressure when the long shaft 5a is ground is uniform over the entire circumference. That is, even if the roundness deteriorates at the CC position in the figure, the AA, BB, DD, and EE positions are not affected, and as a result, the AA line. , BB, DD, and EE, the roundness of each cross section is kept good.

  In the present embodiment, the crankshaft 5 is in the vertical direction, but this does not exclude a mode in which the crankshaft 5 is horizontal or oblique with the same mechanism. Further, it is not excluded that a similar function is achieved by a different mechanism, for example, the electric element 2 is below the compression element 3.

In this embodiment, the description has been made using the rotary compressor as the type of the compressor. However, the present invention is not limited to the rotary compressor, and can be applied to other types of compressors such as a scroll compressor. Needless to say.
In the present embodiment, the relief region 5d is provided with a diameter one step smaller than the finished surface of the long shaft 5a of the crankshaft 5, but it may be provided with a diameter one step larger.

  Thus, as described above, the rotary compressor in the present embodiment is provided with the relief region 5d that is one step smaller than the diameter of the long axis 5a of the crankshaft 5, and the horizontal hole 11 for venting gas having a large diameter is escaped from the vertical hole 9. Since the region 5d is provided so as to communicate with the region 5d, in the grinding finishing of the crankshaft 5, the long shaft 5a has a uniform polishing area over the entire circumference and can be processed with good roundness.

Furthermore, in the present embodiment, the area of the degassing horizontal hole 11 is the same as or larger than that of any of the refueling horizontal holes 10, so that the compressor of the present embodiment is used as a refrigerant compressor. Even when lubricating oil having low mutual solubility with the refrigerant is used, it is avoided that the function of releasing the gas in the degassing side hole 11 is deteriorated due to factors such as adhesion of the lubricating oil to the degassing side hole 11. Thus, sufficient oil supply to the bearing becomes possible.
That is, when the compressor of the present embodiment that can increase the diameter of the degassing lateral hole 11 is used as a hydrofluorocarbon (HFC) refrigerant compressor, the alkylbenzene-based lubricating oil with low mutual solubility is used. In this case, it is possible to prevent the function of the degassing horizontal hole 11 from being deteriorated due to factors such as that the lubricating oil adheres to the degassing horizontal hole 11 and the refrigerant gas is difficult to remove.

  Up to now, it is inferior in terms of lubricity and stability compared to alkylbenzene, and uses an ester-based or ether-based lubricating oil that is mutually soluble in combination with an HFC refrigerant to trap moisture in the refrigerant circuit. However, by using the compressor of the present embodiment, alkylbenzene excellent in lubricity and stability can be used as the lubricating oil, and the reliability of the compressor can be improved. In addition, an apparatus for capturing moisture is not necessary, and the reliability of the compressor can be improved and the cost can be reduced.

  Further, in this embodiment, when the escape area 5d is provided with a diameter one step larger than the finished surface of the long axis 5a of the crankshaft 5, the strength of the escape area 5d is increased, and the gas outlet has a larger diameter. Side holes 11 can be provided, and more efficient degassing can be realized.

  Further, as shown in FIG. 6 of the conventional example, the side hole 11 for venting gas does not serve as the function of the side hole 10 for oil supply. Therefore, the annular annular region 12 for separating the gas and the lubricating oil is formed. In other words, there is no need to fit the degassing lateral hole 11 and the escape area into the long bearing 7, and the degassing lateral hole 11 is opened into the sealed container 1. Therefore, forced gas discharge due to the centrifugal force generated by the rotation of the crankshaft 5 is performed, and the gas can be discharged into the sealed container 1 more efficiently.

Sectional drawing which shows the compressor by Embodiment 1 of this invention. 1 is a cross-sectional view of a main part showing a crankshaft of a compressor according to Embodiment 1 of the present invention. Sectional drawing which shows the conventional compressor. The principal part sectional drawing which shows the crankshaft of the conventional compressor. Sectional drawing which shows the other conventional compressor. The fragmentary sectional view which shows the degassing structure of the crankshaft of the conventional compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container, 2 Electric element, 2a Motor rotor, 3 Compression element, 5 Crankshaft, 5a Long axis, 5b Short axis, 5c Eccentric shaft, 5d Escape area, 5f Roundness deterioration area, 6 Rolling piston, 7 Long bearing , 8 Short bearing, 9 vertical hole, 10 horizontal hole for refueling, 11 horizontal hole for degassing, 12 annular region.

Claims (2)

A compressor having an electric element, a compression element driven by a driving force of the electric element, and a shaft that is rotatably inserted into a bearing and transmits the driving force of the electric element to the compression element The shaft has an opening at one end, a hole drilled along a longitudinal direction, an annular relief region having a diameter different from the diameter of a portion contacting the bearing, and an opening in the relief region. And a communication hole that communicates from the hole to the escape region, wherein the relief region is not fitted into the bearing. The shaft includes an oil supply hole that is drilled so as to communicate with the bearing in a portion that contacts the bearing and feeds lubricating oil, and the area of the communication hole is equal to or greater than the area of the oil supply hole. 2. The compressor according to claim 1, wherein the compressor has a size.

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