JP3253000B2 - Ring seal device for turbocharger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbocharger, and more particularly to a turbocharger ring seal device for preventing lubricating oil of a turbocharger from escaping to a compressor chamber.

[0002]

2. Description of the Related Art Conventionally, a retainer fixed to a housing of a turbocharger, a circular concave portion formed on an end face of the retainer on a lubricating chamber side, and the circular concave portion attached to the retainer are substantially closed. A deflector defining a seal chamber in the shape recess, the deflector having an annular main body and a lubricating oil guiding tongue extending continuously and obliquely downward toward the lubrication chamber. It is known that the tongue piece has an opening for discharging the lubricating oil in the seal chamber on the side of the seal chamber. In such a conventional apparatus, the lubricating oil adhering to the surface of the deflector on the lubrication chamber side flows downward by gravity and is guided from the tongue to the drain. Further, the lubricating oil that has entered the seal chamber beyond the deflector flows down along the inner surface of the circular concave portion of the retainer, and is guided from there through the opening to the drain.

[0003]

However, in the prior art,
Since the tongue piece of the deflector was formed of a flat surface inclined with respect to the main body, the area of the opening was small. Therefore, the lubricating oil that has entered the seal chamber is likely to be delayed from being discharged from the opening, and as a result, the lubricating oil is accumulated in the seal chamber. Therefore,
Conventionally, lubricating oil may leak to the compressor impeller side beyond the turbocharger ring seal device.

[0004]

[Means for Solving the Problems] In view of such circumstances,
The present invention provides a retainer fixed to a housing of a turbocharger, a circular recess formed in a lubrication chamber side end surface of the retainer, and a circular recess attached to the retainer and substantially closing the circular recess. A deflector for defining a seal chamber, wherein the deflector has an annular main body and a lubricating oil guiding tongue extending continuously and obliquely downward toward the lubrication chamber from the main body. In a ring seal device for a turbocharger, in which a seal chamber side of a piece has an opening for discharging lubricating oil in the seal chamber, the tongue piece of the deflector is cut in a plane perpendicular to the axial direction of the main body. The configuration is such that the cross-sectional shape at the time of doing is a mountain shape.

[0005]

According to the above construction, the tongue piece of the deflector has a mountain-shaped cross section, so that the size of the gap between the highest part of the opening and the lowest part (bottom part) of the circular recess is made larger than before. be able to. Therefore, the lubricating oil that has entered the seal chamber can be quickly discharged to the outside of the seal chamber via the opening. Therefore, it is possible to prevent the lubricating oil in the seal chamber from leaking to the compressor impeller side.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the illustrated embodiment. In FIG. 1, a rotary shaft 4 is rotatably supported on a housing 1 of a turbocharger via a radial bearing 2 and a thrust bearing 3. The left end of the rotating shaft 4 is made to protrude from the lubrication chamber 6 into the compressor chamber 7 while maintaining the liquid tightness by the ring seal device 5, and the compressor impeller 8 is fixed to the protruding end. The ring seal device 5 includes a generally cup-shaped retainer 11 fixed to the housing 1, and the rotating shaft 4 passes through a through hole 11 a formed in a shaft portion of the retainer 11. The left end of the rotating shaft 4 has a small diameter portion. The first collar 12, the second collar 13 and the compressor impeller 8 are sequentially fitted to the small diameter portion, and the nut 14 is tightened.
The colors 12, 13 and the compressor impeller 8
Are integrally fixed between the nut 14 and a step 4a formed on the rotating shaft 4. An outer peripheral portion on the left side of the second collar 13 is fitted in the through hole 11a, and
C is inserted into an annular groove 15 provided in the outer peripheral portion on the left side of the collar 13.
The ring 16 is housed. The outer diameter of the C ring 16 is larger than the inner diameter of the through hole 11a of the retainer 11 in a natural state, and the gap between the butting surfaces at both ends of the C ring 16 is reduced to reduce the outer diameter of the through hole 11a. Pressed into. Therefore, the C ring 16 is fixed to the retainer 11 and the second collar 1 is attached to the C ring 16.
3 rotates integrally with the rotating shaft 4. And the second
Gap between collar 13 and through hole 11a, and C ring 1
A non-contact labyrinth is formed by the gap between the lubrication chamber 6 and the annular groove 15, and the lubrication chamber 6 and the compressor chamber 7 are sealed by the labyrinth. The first color 12
A pair of flanges 12a, 1
2a ', whereby an annular groove 12b is formed in the central portion in the axial direction. And this annular groove 12b
Inside, an inner peripheral portion of a thrust bearing 3 fixed to the housing 1 is interposed. As shown in FIG.
Is formed in a C-shape by cutting out about one-fourth in the circumferential direction, and a pair of edges 3a and 3b extending in the radial direction are formed by the cutout. 3a and 3b are located in directions orthogonal to each other. Then, the thrust bearing 3 thus formed is placed so that the edges 3a and 3b are located on the lower side, that is, the edges 3
The inner peripheral portion of the thrust bearing 3 is located in the annular groove 12b of the first collar 12 via the notch portion between a and 3b. As shown in FIG. 1, a sliding surface between the thrust bearing 3 and the annular groove 12 b of the first collar 12 is formed through a lubricating oil passage 17 formed in the housing 1 and a lubricating oil passage 18 formed in the thrust bearing 3. Lubricating oil can be supplied. Lubricating oil can also be supplied to the radial bearing 2 by a lubricating oil passage 19 branched from the passage 17, and the lubricating oil supplied to each of the bearings 2 and 3 flows down in the lubricating chamber 6 to be below the housing 1. Can be discharged to the outside from the drain 20 formed at the bottom. Next, the retainer 11 is fitted into the through hole 23 of the housing 1 from the left side in FIG. 1 and is prevented from falling off by a snap ring 24. A gap between the through hole 23 and the retainer 11 is sealed by an O-ring 25. Has been maintained. As shown in FIG. 1, a circular concave portion 11b centering on the through hole 11a is formed on the end face of the retainer 11 on the side of the lubrication chamber 6, and the circular concave portion 11b is used as a substantial lubricating oil discharging concave portion. I have.
A deflector 26 is attached to the lubrication chamber 6 side of the retainer 11, and the deflector 26
Is substantially closed, and a seal chamber 27 is defined in the circular recess 11b. As shown in FIGS. 2 and 3, the deflector 26 includes an annular main body 26A that substantially covers the circular concave portion 11b, and a tongue extending obliquely downward from the main body 26A to the lubrication chamber 6 side. Piece 26B. The main body 26A includes an inner flat surface 26a, an outer flat surface 26b, and a conical surface 26c connecting them. Then, the outer peripheral portion of the outer flat surface 26b of the main body 26A is fitted into the circular concave portion 11b, and in this state, the circular concave portion 11b is formed.
The deflector 26 is attached to the retainer 11 by caulking a plurality of portions of the edge portion in. In the state after assembly shown in FIG. 1, the inner peripheral portion of the deflector 26 (flat surface 2)
6a) is located on the left side of the first collar 12 and on the outer side in proximity to the second collar 13. FIG.
As shown in FIG. 5, the tongue piece 26B extending obliquely downward in the deflector 26 is in a state of intersecting with the thrust bearing 3 through the cutout portion of the thrust bearing 3. Further, an opening 28 is formed between the tongue piece 26B of the deflector 26 and the circular concave portion 11b. When the lubricating oil enters the sealing chamber 27 from the lubrication chamber 6 side beyond the deflector 26, the lubricating oil in the sealing chamber 27 is guided to the drain 20 through the opening 28. The above-described configuration and operation based on the configuration are not different from those of the related art. In this embodiment, the size of the opening 28 is increased to about twice that of the conventional one by improving the shape of the tongue piece 26B of the deflector 26, and the highest part 26B 'of the opening 28 is This is about twice as high. That is, as shown in FIGS. 2 to 4, the tongue piece 26B of the present embodiment is formed in such a shape that its cross section becomes a mountain shape when cut along a plane parallel to both flat surfaces 26a and 26b of the main body 26A. ing. This tongue piece 26B has the highest height at the central portion which is the boundary with the conical surface 26c in FIG. 2, and its highest portion 26B '.
Has a gradually decreasing height from the highest part 26B 'toward the left and right sides with the same gradient. As shown in FIG. 2, the height of the highest portion 26B 'is set at a height position which does not interfere with the outer peripheral portions of the flange portions 12a and 12a' of the first collar 12 and is as close as possible to the outer periphery. The boundary between the conical part 26c and the flat surface 26b extending from the highest part 26B 'toward the left and right sides is linear, and these boundary parts are both edges 3a, 3a of the thrust bearing 3.
3b so as not to interfere with them. In FIG. 2, the first color 12
If the outer diameters of the flange portions 12a and 12a 'can be reduced, the height of the highest portion 26B' can be increased accordingly, and the boundary extending from the highest portion 26B 'to the left and right also has a thrust bearing 3A. Edges 3a, 3b of
The gradient can be further increased as long as the interference does not occur. Thereby, the size of the opening 28 can be further increased. In contrast to the present embodiment, as shown in FIG.
6B is a flat surface. Therefore, it is difficult to make the opening 28 large, and the height of the highest part is low. Therefore, conventionally,
The lubricating oil that has entered the seal chamber 27 tends to be delayed through the opening 28 to be discharged, and the lubricating oil in the seal chamber 27 passes through the retainer 11 and the second collar 13 and enters the compressor chamber 7. There was something. On the contrary,
According to the above-described embodiment, since the height of the highest portion 26B 'can be increased and the opening 28 can be made large, such a disadvantage can be solved. FIG.
This is a comparison of the oil repellency of the deflector 26 of the present embodiment and the conventional deflector 26 shown in FIG. The testing machine is
This is an acceleration test method for measuring the amount of oil leakage to the intake side of a turbocharger. The test conditions are as follows. Testing machine Turbocharger seal unit testing machine Oil type 10w-30 Oil temperature 80 ± 5 ° C Oil amount 1.2 liter / min Rotation speed 50,000 rpm The vertical axis of FIG. The abscissa indicates the magnitude of the differential pressure between the compressor chamber and the lubrication chamber before and after the ring seal device. As can be understood from FIG. 6, according to the deflector 26 of this embodiment, the leakage amount of the lubricating oil can be reduced by about 40% as compared with the conventional one. 8 to 10 show the result of visually confirming the leakage amount of the lubricating oil into the seal chamber 27. 7 to 10 show a transparent retainer 11.
The result of checking the amount of leakage of the lubricating oil into the seal chamber 27 with the naked eye was prepared by mounting the deflector 26 of the present embodiment and the conventional deflector 26 shown in FIG. Here, FIGS. 7 and 8 show the deflector 2 of this embodiment.
6 shows that no oil leaked to the compressor 7 side beyond the retainer 11 in the initial rotation state of the rotating shaft 4. Also, although lubricating oil has entered the seal chamber 27, as shown in FIG.
About two-thirds are blocked with lubricating oil, but the remaining one-third
The degree remained open. FIGS. 9 and 10 show a case where a conventional deflector 26 is used in this embodiment, and the rotating shaft 4 starts rotating and enters a steady operation state after a lapse of several tens of seconds. At this point, the entire area of the opening 28 is closed by the lubricating oil and the sealing chamber 27 is closed.
Lubricating oil accumulated in more than half of the inside, and oil leaked into the compressor chamber 7 beyond the retainer 11 was observed. As described above, according to the present embodiment, the tongue piece 26B of the deflector 26
Can be formed to have a chevron cross section to increase the height of the highest portion 26B 'and increase the size of the opening 28, so that the lubricating oil that has penetrated into the seal chamber 27 through the opening 28, It can be discharged quickly. Moreover, according to the present embodiment, as shown by the imaginary line in FIG. 3, as compared with the case where the flat tongue similar to the conventional one shown in FIG. Thus, the infiltration of the lubricating oil into the seal chamber 27 can be satisfactorily prevented. That is,
In the conventional shape shown by the imaginary line in FIG. 3, a relatively large triangular gap 40 is formed not only below the tongue piece 6B (imaginary line) but also at positions on both sides of the tongue piece 6B. Become. On the other hand, when the tongue piece 6B of the present embodiment shown by the solid line is adopted, the gap 40 on both sides of the tongue piece 6B becomes small.
As described above, the gap 40 can be reduced, so that the oil that has flowed down the wall of the deflector 26 on the lubrication chamber 6 side to the position of the gap 40 enters the seal chamber 27 through the gap 40. It becomes difficult. This allows
Even when the pressure in the seal chamber 27 becomes a negative pressure more instantaneously than that in the lubrication chamber 6, it is possible to satisfactorily prevent the oil from being sucked through the gap 40 and entering the seal chamber 27 due to the negative pressure. Can be. Therefore, it is possible to prevent the lubricating oil in the seal chamber 27 from leaking to the compressor impeller 8 side.

[0007]

As described above, according to the present invention, it is possible to obtain an effect that the lubricating oil that has entered the seal chamber can be quickly discharged to the outside of the seal chamber through the opening.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a sectional view of a main part taken along line II-II in FIG. 1;

FIG. 3 is a front view of the deflector shown in FIG. 2;

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

FIG. 5 is a front view of a conventional deflector.

FIG. 6 is a diagram comparing the performance of the present invention and a conventional deflector.

FIG. 7 is a cross-sectional view of a main part showing an experimental result using the deflector of the present invention.

8 is a view of the experimental result of FIG. 7 as viewed from the left side.

FIG. 9 is a cross-sectional view of a main part showing an experimental result using a conventional deflector.

FIG. 10 is a view of the experimental result of FIG. 9 as viewed from the left side.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Housing 5 ... Ring seal device 6 ... Lubrication room 7 ... Compressor room 11 ... Retainer 11b ... Circular recess 26 ... Deflector 26B ... Tongue piece 28 ... Opening

Continuation of front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F02B 39/14 F02B 39/00

Claims (2)

(57) [Claims] 1. A retainer fixed to a housing of a turbocharger, a circular concave portion formed on an end face of the retainer on a lubrication chamber side, and a circular concave portion attached to the retainer, substantially closing the circular concave portion. A deflector defining a seal chamber therein, the deflector having an annular main body and a lubricating oil guiding tongue extending continuously obliquely downward toward the lubrication chamber from the main body. In a ring seal device for a turbocharger in which the tongue piece has an opening for discharging lubricating oil in the seal chamber, the tongue piece of the deflector is disposed on a plane orthogonal to the axial direction of the main body. A ring seal device for a turbocharger, wherein a cross-sectional shape when cut is formed into a mountain shape. 2. A collar having a shaft portion fitted on the outer periphery of the rotary shaft and a flange portion slidably contacting the surface of the thrust bearing is disposed closer to the lubrication chamber than the deflector. An inner peripheral portion of a C-shaped thrust bearing having a portion cut off in a circumferential direction is located at a position adjacent to a flange portion of the collar, and a tongue piece of the deflector is provided with an outer peripheral portion of the flange portion of the collar and the thrust bearing. 2. The ring seal device for a turbocharger according to claim 1, wherein the ring seal device has a mountain-shaped cross section as long as it does not interfere with both radially extending edges of the notch portion of the bearing. 3.