JPH0119078B2 - - Google Patents

Description

[Detailed Description of the Invention] [Object of the Invention] (Industrial Application Field) The present invention relates to a rotary compressor, and in particular, to reducing the amount of leakage of refrigerant gas from the rotary compressor to increase its volumetric efficiency. The present invention relates to a rotary compressor that can increase the cooling capacity and coefficient of performance of a refrigerator using the rotary compressor as much as possible.

(Prior art) In general, the rotating shaft and sliding parts of a compressor are lubricated, but the drive shaft of the roller in a rotary compressor, especially the subshaft below the cylinder, is lubricated conventionally. , was done as follows.

As shown in FIG. 1, the roller 2 provided in the cylinder 1 is provided so as to fit into the eccentric portion 3a of the drive shaft 3, and its center axis Or is provided eccentrically with respect to the rotation axis O. . The drive shaft 3 has a main shaft part 4 above the eccentric part 3a and a sub-shaft part 5 below, and is supported by a main bearing 6 or a sub-shaft bearing 7, respectively. A lubricating oil groove 9 is formed in the bearing surface 8 of the sub-bearing 7 along the axial direction, and the opening 10 of the groove faces the inside of the cylinder 1 and is connected to the thrust portion 11 and the lower end surface of the roller 2 along with the bearing surface 8. The seal portion 12 is also configured to supply lubricating oil. In addition, if the lubricating oil 9 is formed straight in the axial direction as shown in FIG. The lubricating oil is supplied to the lubricating oil groove 9 through the lubricating oil groove 13, and the lubricating oil is supplied to the bearing surfaces 8, 11 and the seal portion 12.

By the way, the lubricating oil groove 9 of the sub-bearing 7 was generally provided on the opposite side of the load direction in order to form an effective oil film on the bearing surface 8. That is, the second
As shown in the figure, the load acting on the roller 2 acts from the compression chamber 14 side where the pressure is high to the suction chamber 15 side where the pressure is low.
Since the contact pressure with the bearing surface 8 on the side opposite to the load direction is high, an oil film must be formed well on this suction side. In this case, the lubricating oil interposed between the subshaft portion 5 and the bearing surface 8 escapes from the lubricating oil groove 9, and sufficient oil film pressure cannot be obtained, making galling due to metal contact likely to occur. Therefore, the lubricating oil groove 9 and its cylinder side opening 10 were provided on the compression chamber 14 side where the contact pressure is low.

(Problem to be Solved by the Invention) However, the thrust part 11 and the seal part 1
The pressure difference between the inside of the compression chamber 14 and the cylinder side opening 10 of the lubricating oil groove 9, which affects the amount of lubricating oil or seal oil supplied to the lubricating oil groove 9, is not so large, and it is difficult to obtain a sufficient amount of lubricating oil or seal oil. Ta. Particularly, the seal portion 12 (indicated by hatching in the figure) on the side of the suction chamber 15 requires a special amount of oil supply, and since a sufficient amount of oil supply cannot be secured in this part, the high-pressure refrigerant in the inner peripheral space of the roller 2 is Gas flows from the seal part 12 to the suction chamber 15
As a result, the amount of refrigerant gas sucked into the suction chamber 15 decreases, reducing the volumetric efficiency of the rotary compressor or the refrigerating capacity of the refrigerator using this rotary compressor, and furthermore, the coefficient of performance also decreases. There was a problem that caused this.

The present invention has been devised in view of the above problems and to effectively solve them.

The purpose of the present invention is to reduce the amount of leakage of refrigerant gas from a rotary compressor and increase its volumetric efficiency as much as possible, thereby increasing the refrigerating capacity and coefficient of performance of a refrigerator using this rotary compressor. The object of the present invention is to provide a rotary compressor that can increase the speed.

[Structure of the Invention] (Means for Solving the Problem) In order to achieve the above object, the present invention includes a cylindrical cylinder, a roller that rolls on an inner circumferential wall surface of the cylinder, and a diameter of the cylinder. In the rotary compressor, the rotary compressor is equipped with a blade that is urged inward in a direction and is always in contact with the roller, and a main bearing and a sub-bearing that pivotally support the drive shaft of the roller above and below the cylinder. The cylinder side opening of the oil supply passage formed in the bearing surface is provided within a range of a center angle of 0° to 60° from the blade in the rotational direction of the drive shaft.

(Function) According to the above configuration, the rotation of the drive shaft causes lubricating oil to flow into the oil supply passage by the centrifugal pump mechanism, and is supplied to the inner peripheral space of the roller from the cylinder side opening. At this time, by locating the opening on the cylinder side of the oil supply passage in the range of 0 to 60 degrees from the blade in the rotation direction, a larger pressure difference can be obtained during oil supply than in the case of conventional installation on the compression side. The bearing surface of the auxiliary bearing can be well lubricated without reducing the efficiency or capacity of the compressor, and the seal portion of the roller can be sufficiently lubricated.

(Embodiment) A preferred embodiment of the present invention will be described below with reference to the accompanying drawings.

As shown in FIG. 3, a cylindrical cylinder 1 is provided with a roller 2 that rolls on an inner circumferential wall surface 16 thereof. The roller 2 is fitted into an eccentric portion 3a of a drive shaft 3 that rotationally drives the roller 2, and its center
Or is provided eccentrically with respect to the axis O of the drive shaft 3. Further, a plate-shaped blade 17 that is urged inward from the outside in the radial direction of the cylinder 1 is always in contact with this roller 2.
The inside of the cylinder 1 is divided by 7 to form a compression chamber 14 and a suction chamber 15.

By the way, the drive shaft 3 of the roller 2 is supported by an auxiliary bearing 7 below the cylinder 1, and a bearing surface 8 (shown in FIG. 1) of this auxiliary bearing 7 is provided with lubricating oil to the suction chamber side. A lubricating oil groove 9 (shown in FIG. 1) is formed as a lubricating oil passage 19 for penetration. That is, the cylinder side opening 10 is provided on the suction chamber 15 side, and specifically, the blade 17 is rotated in the rotational direction (clockwise direction in the illustrated example) about the axis O of the drive shaft 3. It is provided at a central angle θ from the center. This central angle θ is set within the range of 0° to 60°, but in this embodiment, θ=60°.

Next, the operation of the present invention will be explained.

First, general lubricating oil supply will be explained with reference to FIG.

When the drive shaft 3 rotates, lubricating oil stored at the bottom of a casing (not shown) is supplied from the inside of the subshaft 5 to the shaft oil hole 13 by a suitable centrifugal pump mechanism that utilizes the rotation of the drive shaft 3. The lubricating oil is further pressurized on the inner wall surface of the oil hole 13 and flows into the oil supply passage 1.
9 is sent to the lubricating oil groove 9. This lubricating oil is divided upward and downward within the lubricating oil groove 9, and the downward lubricating oil lubricates between the outer peripheral surface of the subshaft portion 5 and the bearing surface 8 of the subbearing 7, and returns to the bottom of the casing.

On the other hand, the upward lubricating oil lubricates the thrust part 11 and is sent into the inner peripheral space of the roller 2 when the thrust part 11 opens the cylinder side opening 10. The lubricating oil in the inner peripheral space of the roller 2 is effectively supplied to the seal portion 12 of the roller 2 due to the large pressure difference between the inner peripheral space of the roller 2 and the suction chamber 15.

That is, in FIG. 3, the suction chamber 15 increases its volume as the roller 2 rolls clockwise on the inner circumferential wall surface 16 of the cylinder 1, and its internal pressure decreases in order to suck refrigerant gas. Become. Conversely, the compression chamber 14 decreases its volume and increases its internal pressure. Let the respective internal pressures be P ₄ (on the suction chamber 15 side) and P ₀ (on the compression chamber 14 side), and let the pressure at the cylinder side opening 10 of the lubricating oil groove 9 (shown in Figure 1) be P ₁ , and the respective pressures will be Comparing the difference, P ₁ - P ₄ > P ₁ - P ₀ , and by providing the cylinder side opening 10 on the suction chamber 15 side, a larger pressure difference can be obtained than in the conventional case where it is provided on the compression chamber 14 side. It will be done.
Therefore, the suction chamber 15 of the seal portion 12 of the roller 2
It is possible to supply oil directly to the side (shown by hatching in FIG. 3), and a sufficient amount of oil can be ensured to ensure airtightness.

As a result, the suction chamber 1 is removed from the inner peripheral space of the roller 2.
The amount of refrigerant leaking to the fuel cell 5 will be reduced, and the volumetric efficiency will be improved.

Therefore, in a refrigerator employing the rotary compressor according to the present invention, its refrigerating capacity and coefficient of performance are improved. FIG. 6 shows the experimental data, and according to the present invention, a higher value of 1 to 2% in refrigerating capacity and 2 to 4% higher value in coefficient of performance was obtained than in the conventional method. (In Figure 6, the horizontal axis is
The position of the blade 17 is set at 0° with respect to the axis O of the drive shaft 3, and the central angle θ of the position of the cylinder side opening 10 is shown with the rotation direction as positive and the opposite as negative. Furthermore, if the central angle θ is 60° or more, it will impede the formation of a lubricating oil film on the subshaft 5 (shown in Figure 1), increasing the input to the drive shaft 3 and lowering the coefficient of performance. are doing. Further, when the lubricating oil groove 9 is formed in a helical shape, the shaft oil hole 13 is not necessarily necessary because it has a pumping effect by itself.

As shown in FIGS. 4 and 5, the lubricating oil groove 9 is located on the compression chamber 14 side, and the roller 2 is located on the suction chamber 15 side at the cylinder side end of the sub bearing 7.
Effects similar to those of this embodiment can be obtained by providing the cutout portions 18 as the oil supply passages 19 so as not to cover the seal portions 12 on the upper and lower end faces of the oil supply passage 19. Further, the notch portion 18 may be provided on the main shaft portion 4 side.

[Effects of the Invention] As is clear from the above description, the present invention provides the following excellent effects.

(1) The amount of refrigerant gas leaking from the inner peripheral space of the suction chamber roller of the rotary compressor can be reduced.

(2) Therefore, the refrigeration capacity and coefficient of performance of the refrigerator using the rotary compressor can be increased as much as possible.

(3) The structure is simple and can be easily adopted.

[Brief explanation of drawings]

FIG. 1 is a side cross-sectional view showing a schematic configuration of a rotary compressor, FIG. 2 is a plan view showing the position of the cylinder-side opening of a conventional lubricating oil groove, and FIG. 3 is a cylinder of a lubricating oil groove according to the present invention. FIG. 4 is a plan view showing an embodiment of the side opening, FIG. 4 is a plan view showing a modified embodiment of the present invention, FIG. 5 is a side sectional view of the main part of FIG. 4, and FIG. 6 is a cylinder of the lubricating oil groove. It is a graph of experimental data showing the relationship between the position of the side opening, the refrigerating capacity, and the coefficient of performance. In the figure, 1 is a cylinder, 2 is a roller, 3 is its drive shaft, 7 is a sub-bearing, 9 is a lubricating oil groove, 10 is an opening on the cylinder side, 15 is a suction chamber, 17 is a blade, 18 is a notch, 19 is an oil supply passage, and O is the axis of the drive shaft.

Claims (1)

[Claims] 1 A cylindrical cylinder, a roller that rolls on the inner peripheral wall surface of the cylinder, a blade that is urged inward in the radial direction of the cylinder and constantly contacts the roller, and a drive shaft of the roller that is connected to the cylinder. In a rotary compressor equipped with a main bearing and a sub-bearing that are pivotally supported above and below, the cylinder side opening of the oil supply passage formed on the bearing surface of the sub-bearing is rotated about the axis of the drive shaft. A rotary compressor, characterized in that the rotary compressor is provided with a central angle within a range of 0° to 60° from the blade in the direction.