JP2008190680A - Floating bush bearing structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce vibration and noise caused by the self-excited vibration of a rotating shaft by changing the shape of a floating bush. <P>SOLUTION: In this floating bush bearing structure, the cylindrical floating bush is disposed between the rotating shaft and a housing, and the rotating shaft is rotatably supported on the housing through the oil film formed on the inner peripheral side and the outer peripheral side of the floating bush. The floating bush 8 is reduced in thickness by forming oil supply holes 10b radially extending through a floating bush body 11 at unequal intervals B in addition to oil supply holes 10 radially extending therethrough at equal intervals A therethrough. Since the left side weight of the floating bush body is reduced and the weight unbalance amount in the circumferential direction is formed, a bush 12 with unbalanced weight is formed. Since the center of gravity W is displaced to the right side of a reference line 13 passing through the center O of the floating bush body 11 due to a lateral weight unbalance, the self-excited vibration can be suppressed. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a floating bush bearing structure capable of reducing vibration and noise due to self-excited vibration of a rotating shaft.

  FIG. 12 shows the overall configuration of the turbocharger. In the turbocharger, the turbine chamber 3 for accommodating the turbine 2, the compressor chamber 5 for accommodating the compressor 4, and the turbine 2 and the compressor 4 are connected in the housing 1. A rotating shaft chamber 7 in which the rotating shaft 6 is disposed, and the rotating shaft 6 is a bearing comprising a floating bush 8 disposed at a distance from the turbine 2 side and the compressor 4 side of the rotating shaft chamber 7. The structure is rotatably supported by the housing 1. The turbine 2 is driven by the energy of the exhaust gas from the engine, and the intake air sent to the engine is compressed and supplied to the engine by the compressor 4 that rotates integrally with the turbine 2.

  The housing 1 is formed with an oil supply path 9 for supplying lubricating oil from an oil pump, which is an oil supply source (not shown), to the floating bush 8.

  The floating bush 8 has a slight gap between the outer peripheral surface of the rotary shaft 6 and the inner peripheral surface of the housing 1 (for example, a diameter of about 40 to 60 μm and a radius of about 20 to 30 μm). The gap is smaller than the gap between the floating bush 8 and the housing 1.) and is formed by a substantially cylindrical floating bush main body 11 that fits and is further floated as shown in FIGS. At the center position of the cylindrical axial length of the bush main body 11, a plurality of oil supply holes 10 are formed at equal intervals A in the circumferential direction and having the same diameter and penetrating in the radial direction. A supply port 9 a branched from the oil supply path 9 of the housing 1 is opened so as to face the oil supply hole 10 of each floating bush 8.

  Accordingly, the lubricating oil supplied from the oil supply passage 9 to each floating bush 8 via the supply port 9 a is first supplied to the outer periphery of the floating bush 8, and the outer peripheral surface of the floating bush 8 and the inner peripheral surface of the rotary shaft chamber 7. An oil film on the outer peripheral side is formed in a gap between the inner surface of the floating bush 8 and the outer peripheral surface of the rotary shaft 6 through the oil supply hole 10. The oil film is supplied to the gap and forms an oil film on the inner peripheral side, and then flows into the rotating shaft chamber 7.

  Accordingly, the floating bush 8 is held in a floating state between the rotary shaft 6 and the housing 1 by the outer peripheral oil film and the inner peripheral oil film, and rotates less than the rotational speed of the rotary shaft 6 as the rotary shaft 6 rotates. The rotating shaft 6 is rotatably supported with respect to the housing 1 via an oil film while rotating (rotating) by a number.

  As described above, the conventional floating bush 8 has a plurality of oil supply holes 10 formed at equal circumferential positions A as described above. Therefore, the conventional floating bush 8 has a center O and a center of gravity W that are the same. Thus, the circumferential weight is balanced, and the floating bush 8 itself is prevented from vibrating.

As the above-mentioned floating bush bearing structure, there are those shown in Patent Document 1 and Patent Document 2.
JP 2002-332864 A JP 2006-177487 A

  In recent years, turbochargers for automobiles, in particular, have been increased in supercharging and speeding up, and their rotational speed has reached 200 to 300,000 rpm.

  Unlike the mode characteristics (such as rotational primary vibration) caused by mechanical unbalance, the rotating shaft and its bearing system that rotate at high speeds like this have an oil whirl that continuously vibrates according to the natural vibration characteristics of the system (oil -whirl) and self-excited vibration called oil-whip. This self-excited vibration is mainly generated when the shafts of the rotary shaft 6, the floating bush 8 and the housing 1 are made to coincide with each other, that is, when the eccentricity ratio is reduced as in the conventional floating bush bearing structure. .

  Therefore, as shown in FIGS. 13 and 14, there is a limit in trying to prevent or reduce the occurrence of self-excited vibration by using the floating bush 8 having a balanced weight in the circumferential direction, and the self-excited vibration is effectively reduced. I can't let you. For this reason, in a turbocharger for automobiles that requires high speed and quietness, there is a problem that the self-excited vibration and the vibration noise accompanying it cause discomfort to the passenger.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a floating bush bearing structure in which vibration and noise due to self-excited vibration of the rotating shaft can be reduced by changing the shape of the floating bush. is there.

  In the present invention, a cylindrical floating bush is disposed between a rotating shaft and a housing, and the rotating shaft is rotatably supported on the housing via an oil film formed on the inner peripheral side and the outer peripheral side of the floating bush. The present invention relates to a bush bearing structure, wherein the floating bush is constituted by a weight unbalance bush having a weight unbalance amount in a circumferential direction in a floating bush body.

  In the floating bush bearing structure, it is preferable that the weight unbalance bush has a circumferential weight unbalance amount that does not contact the rotating shaft and the housing due to a centrifugal force generated by the rotation of the weight unbalance bush.

  Further, in the above floating bush bearing structure, the weight unbalance bush is formed in the floating bush body by forming an oil supply hole having a uniform aperture and having a uniform aperture in the circumferential direction and penetrating in the radial direction. The weight unbalance amount can be provided.

  In the above-described floating bush bearing structure, the weight unbalance bush has a circumferential weight by forming, in the floating bush body, oil supply holes that are circumferentially spaced at equal intervals and unequal in diameter. An unbalance amount can be provided.

  In the above-described floating bush bearing structure, the weight unbalance bush penetrates the floating bush main body into a floating bush main body formed with oil supply holes having a uniform bore and a uniform diameter in the circumferential direction and penetrating in the radial direction. Alternatively, it is possible to provide a weight unbalance amount in the circumferential direction by forming a weight adjusting hole that does not penetrate.

  Further, in the above-described floating bush bearing structure, the weight unbalance bush has a weight adjustment notch formed in the floating bush main body formed with oil supply holes that penetrate in the radial direction and have a uniform aperture in the circumferential direction. By doing so, a weight unbalance amount in the circumferential direction can be provided.

  In the above-described floating bush bearing structure, the weight unbalanced bush is mounted with a weight adjusting dissimilar member on a floating bush main body having a uniform bore in the circumferential direction and an oil supply hole penetrating in the radial direction. Thus, a weight unbalance amount in the circumferential direction can be provided.

  The floating bush bearing structure can be applied to a turbocharger bearing structure.

  According to the floating bush bearing structure of the present invention, since the floating bush is constituted by the weight unbalance bush having the weight unbalance amount in the circumferential direction, the weight unbalance bush is centered on the rotating shaft by the centrifugal force caused by the rotation. On the other hand, it becomes eccentric and swings. For this reason, a portion where the gap becomes small occurs between the rotating shaft and the weight unbalance bush, and pressure is generated by the squeeze effect of the oil film in the portion where the gap becomes small, thereby pushing the rotating shaft in the radial direction. Force is generated. Further, since the floating bush rotates at a rotational speed smaller than that of the rotating shaft along with the rotating shaft rotating at a high speed, the force pushing the rotating shaft by the squeeze effect acts in succession at different positions in the circumferential direction of the rotating shaft. Therefore, since the rotating shaft receives a force from the outside in the circumferential direction at a different period from the self-excited vibration, the self-excited vibration is suppressed, and therefore, an excellent effect that the vibration and noise are greatly reduced is achieved. obtain.

  Further, since the weight unbalance bush can be easily formed by processing the floating bush body, there is an effect that the floating bush bearing structure capable of reducing vibration and noise due to self-excited vibration can be implemented at low cost.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a front view showing an example of a weight unbalance bush which is a floating bush embodying the present invention, and FIG. 2 is a cross-sectional view in the II-II direction of FIG. At the center of the cylindrical axial length of the bush body 11, the oil supply hole 10 that penetrates in the radial direction with an equal interval A, and the radius with an unequal interval B that is smaller than the equal interval A By forming the oil supply holes 10a and 10b penetrating in the direction, the weight unbalance amount in the circumferential direction is provided, that is, the weight unbalance in which the position of the center of gravity W is shifted from the center O of the floating bush body 11 by a required amount. A bush 12 is formed.

  As shown in FIG. 1, when the oil supply holes 10a and 10b are positioned on the left side of the weight unbalance bush 12 with respect to a virtual reference line 13 passing through the center O of the floating bush body 11, the left side is The light weight side and the right side become the weight side, and the left and right weight imbalance becomes the largest. That is, in this weight unbalanced bush 12, the portions where the oil supply holes 10a and 10b are formed at the unequal intervals B smaller than the equal intervals A are reduced in thickness than the other portions, and the weight is reduced. A weight imbalance occurs.

  When the length of the unequal interval B of the oil supply holes 10a, 10b is shortened, the left and right imbalance increases, and when the length of the unequal interval B is brought closer to the length of the equal interval A, The left and right imbalance is reduced. Further, when the diameters of the oil supply holes 10a and 10b are increased, the left and right imbalances are increased, and when the diameters of the oil supply holes 10a and 10b are decreased, the left and right imbalances are decreased. Although FIG. 1 shows a case where two adjacent oil supply holes 10a and 10b are formed at unequal intervals B, three or more adjacent oil supply holes may be formed at unequal intervals B.

  FIG. 3 is a front view showing another example of a weight unbalance bushing which is a floating bush embodying the present invention, and FIG. 4 is a sectional view in the IV-IV direction of FIG. The floating bush body 11 is formed with oil supply holes 10 having a uniform aperture A in the circumferential direction and having a uniform diameter and penetrating in the radial direction, and further, an intermediate position (A The weight adjusting hole 14 penetrating in the radial direction is formed at the position / 2) to provide a weight unbalance amount in the circumferential direction, that is, the position of the center of gravity W with respect to the center O of the floating bush body 11 is required. An unbalanced weight unbalance bush 12 is formed.

  As shown in FIG. 3, when the weight adjusting hole 14 is positioned on the left side with respect to a virtual reference line 13 passing through the center O of the floating bush body 11, the weight unbalanced bush 12 The light weight side and the right side become the weight side, and the left and right weight imbalance becomes the largest. That is, in the weight unbalance bush 12, the portion where the weight adjusting hole 14 is formed at the intermediate position between the oil supply holes 10c and 10d is thinner than the other portions and the weight is reduced. Balance arises.

  When the diameter of the weight adjusting hole 14 is increased, the left and right unbalance is increased, and when the diameter of the weight adjusting hole 14 is decreased, the left and right unbalance is decreased. Although FIG. 3 shows the case where the weight adjusting hole 14 is penetrated in the radial direction of the floating bush main body 11, it is required on the outer peripheral side or inner peripheral side of the floating bush main body 11 without penetrating the floating bush main body 11. The weight adjusting hole 14 having a depth of 5 mm may be formed, and the position may be shifted from a position of 1/2 (A / 2) of the equal interval A between the two adjacent oiling holes 10c and 10d. The weight adjusting hole 14 may be formed. Further, as shown in phantom lines in FIGS. 3 and 4, the weight unbalance bush 12 is configured by forming a weight adjusting hole 14 ′ in the floating bush body 11 parallel to the axis of the floating bush body 11. May be.

  FIG. 5 is a front view showing still another example of a weight unbalance bush which is a floating bush embodying the present invention, and FIG. 6 is a sectional view in the VI-VI direction of FIG. 5 and has a substantially circular cylindrical shape. In the circumferential position of the floating bush main body 11, an oil supply hole 10 that penetrates in the radial direction with an equal interval A is formed, and further, one oil supply hole 10 is provided on the outer peripheral side of the floating bush main body 11. By forming the large diameter portion 15 so as to sit down at a depth, a weight unbalance amount in the circumferential direction is provided, that is, a weight in which the position of the center of gravity W deviates from the center O of the floating bush body 11 by a required amount. An unbalanced bush 12 is formed.

  In the weight unbalance bush 12, as shown in FIG. 5, the oil supply hole 10 in which the large diameter portion 15 is formed is located on the left side with respect to a virtual reference line 13 passing through the center O of the floating bush body 11. In such a case, the left side is the lightweight side and the right side is the weight side, and the left and right weight imbalance is the largest. That is, in this weight unbalance bush 12, the portion where the large-diameter portion 15 is formed in the oil supply hole 10 is thinner than the other portions and the weight is reduced, so that the weight is unbalanced.

  When the diameter of the large diameter portion 15 is increased or the depth to be formed is increased, the left and right imbalance is increased, and when the diameter of the large diameter portion is decreased or the depth to be formed is reduced, The left and right imbalance becomes smaller. 5 shows the case where the large-diameter portion 15 is formed in one oil supply hole 10 on the outer peripheral side of the floating bush main body 11, but the large diameter is provided in one oil supply hole 10 on the inner peripheral side of the floating bush main body 11. The portion 15 may be formed, or the large-diameter portion 15 may be formed in two or more adjacent oil supply holes 10. Furthermore, instead of forming the large-diameter portion 15 by spot facing or the like in the oil supply hole 10, the diameter of one or two or more adjacent oil supply holes 10 itself is larger than the diameter of the other oil supply holes 10. You may make it form.

  FIG. 7 is a front view showing still another example of a weight unbalance bush which is a floating bush embodying the present invention, and FIG. 8 is a sectional view taken along the line VIII-VIII of FIG. In the circumferential position of the floating bush body 11, an oil supply hole 10 that penetrates in the radial direction with an equal interval A is formed, and further, a portion between two adjacent oil supply holes 10 e and 10 f is provided as an oil supply hole. The weight adjusting notch 16 is cut in the shape of a long hole with the same width as the diameters of 10e and 10f, thereby providing a weight unbalance amount in the circumferential direction, that is, the center of gravity with respect to the center O of the floating bush body 11 A weight unbalance bush 12 is formed in which the position of W is shifted by a required amount.

  The weight unbalance bush 12 is obtained when the weight adjustment notch 16 is positioned on the left side with respect to a virtual reference line 13 passing through the center O of the floating bush body 11 as shown in FIG. The left side is the lightweight side, the right side is the heavy side, and the left and right weight imbalance is the largest. That is, in this weight unbalance bush 12, the portion where the weight adjusting notch 16 is formed is thinner than the other portions and the weight is reduced, resulting in a weight imbalance.

  When the width of the weight adjustment notch 16 is increased, the left and right imbalance increases, and when the width of the weight adjustment notch 16 is reduced, the left and right imbalance decreases. Although FIG. 7 shows the case where the elongated hole-shaped weight adjustment notch 16 is formed between the oil supply holes 10e, 10f, the weight adjustment is performed by processing one oil supply hole 10 into a long hole shape. The notch 16 may be formed.

  9 is a front view showing still another example of a weight unbalance bush which is a floating bush embodying the present invention, and FIG. 10 is a sectional view taken along the line XX of FIG. 9 and has a substantially circular cylindrical shape. In the circumferential position of the floating bush main body 11, an oil supply hole 10 that penetrates in the radial direction with an equal interval A is formed, and two adjacent oil supply holes 10 g are formed on the inner peripheral side of the floating bush main body 11. , 10h, a non-penetrating hole 17 having a required diameter and depth is formed, and a weight adjusting heterogeneous member 18 formed of a material having a specific gravity greater than that of the floating bush body 11 is inserted into the hole 17. Thus, the weight unbalance bush 12 having a circumferential weight unbalance amount, that is, the center of gravity W being displaced from the center O of the floating bush main body 11 by a required amount is formed.

  This weight unbalance bush 12 is obtained when the weight adjusting heterogeneous member 18 is positioned on the right side with respect to a virtual reference line 13 passing through the center O of the floating bush body 11 as shown in FIG. The left side is the lightweight side, the right side is the heavy side, and the left and right weight imbalance is the largest. In other words, in this weight unbalance bush 12, the portion where the weight adjusting heterogeneous member 18 is fixed increases in weight as compared with the other portions, thereby causing weight imbalance.

  When the weight adjusting different member 18 having a specific gravity larger than that of the floating bush main body 11 is fixed or the volume of the weight adjusting different member 18 is increased, the left and right imbalance becomes larger, and slightly more than the floating bush main body 11. When the weight adjusting dissimilar member 18 having a large specific gravity is fixed or the volume of the weight adjusting dissimilar member 18 is reduced, the left and right unbalance is reduced. The weight adjusting dissimilar member 18 is preferably provided on the inner peripheral side of the floating bush main body 11 because centrifugal force acts on the weight adjusting different member 18, but if it can be securely fixed, it is provided on the outer peripheral side of the floating bush main body 11. It may be provided, and the size, shape, mounting position, etc. of the weight adjusting different member 18 can be arbitrarily selected.

  FIG. 11 is a front view schematically showing the operation of the weight unbalance bush 12 of each embodiment described above. In FIG. 11, a weight increasing portion 19 indicated by a black dot is provided on the floating bush main body 11 in order to simplify the explanation. The case where the weight unbalance bush 12 which is provided and caused the weight unbalance is fitted to the outer peripheral surface of the rotating shaft 6 so as to form the oil film 20 is shown.

  When the rotary shaft 6 rotates at a high speed in the direction of the arrow, the weight unbalance bush 12 rotates in the same direction at a rotational speed smaller than the rotary shaft 6 as the rotary shaft 6 rotates. Since the weight unbalance bush 12 has a weight unbalance in the circumferential direction (the position of the center of gravity W is shifted with respect to the center O of the floating bush body 11), the centrifugal force caused by the rotation causes the center of the rotary shaft 6 to be rotated. To start swinging. In FIG. 11, the weight increasing portion 19 is located on the right side with respect to the virtual reference line 13 passing through the center O of the floating bush body 11, the left side is the lightweight side, the right side is the weight side, and the weight unbalance bush 12 is It is eccentric to the weight side with respect to the axis Z of the rotating shaft 6.

  At this time, the weight unbalance amount in the circumferential direction provided in the weight unbalance bush 12 of each embodiment is such that the weight unbalance bush 12 that swings eccentrically with respect to the center of the rotation shaft 6 does not contact the rotation shaft 6 and the housing 1. It is set to be a weight unbalance amount.

  When the weight unbalance bush 12 is eccentric and swings, the inner peripheral surface on the light weight side of the weight unbalance bush 12 approaches the outer peripheral surface of the rotary shaft 6, so that there is a gap with the rotary shaft 6 on the left side as shown in FIG. A reduced portion 21 is produced. Since the oil film 20 is formed between the rotating shaft 6 and the weight unbalance bush 12, the pressure P is generated by the squeeze effect of the oil film 20 by the portion 21 where the gap is reduced. A force F that pushes the rotating shaft 6 rotating at high speed around the center Z in the radial direction (weight side) is generated. At this time, the weight unbalance bush 12 generates a pressure p between the weight unbalance bush 12 and the housing 1 due to the squeeze effect of the oil film due to the weight-side outer peripheral surface approaching the inner peripheral surface of the housing 1. However, since the clearance between the housing 1 and the weight unbalance bush 12 is originally larger than the clearance between the rotary shaft 6 and the weight unbalance bush 12, P> p, and F = P−p This acts on the rotating shaft 6.

  Furthermore, since the weight unbalance bush 12 rotates at a rotational speed smaller than the rotational shaft 6 along with the rotational shaft 6 rotating at high speed, the force F pushing the rotational shaft 6 by the squeeze effect is applied to the rotational shaft 6. Since the rotary shafts 6 are successively applied to different positions in the circumferential direction, the rotating shaft 6 receives the force F from the outside in the circumferential direction at a period different from the self-excited vibration, and thus the self-excited vibration is suppressed. As a result, vibration and noise due to self-excited vibration are greatly reduced.

  Further, as shown in the above embodiments, the weight unbalance bush 12 can be easily formed by processing the floating bush body 11, so that the floating bush bearing structure in which vibration and noise due to self-excited vibration are reduced can be made inexpensive. Can be implemented.

  In addition, the weight unbalance bush 12 may have an unbalance amount in which the weight side is larger by several percent (for example, about 2 percent) than the lightweight side with respect to the entire weight. When rotating at a high speed of about 500,000 to 100,000 rpm, the centrifugal force acting on the weight unbalance bush 12 is large, and when the weight unbalance bush 12 swings, the force F pushing the rotating shaft 6 in the radial direction by the squeeze effect is large. Since the self-excited vibration of the rotating shaft 6 can be suppressed, the weight unbalanced amount of the weight unbalanced bush 12 is a few percent difference between the weight on the light side and the weight side to the weight unbalanced bush 12 is the rotating shaft 6 and the housing 1. The amount of weight unbalance in a range that does not come into contact with can be made.

  Of course, the floating bush bearing structure of the present invention can be applied to other than the turbocharger bearing structure, and various modifications can be made without departing from the scope of the present invention.

It is a front view which shows an example of the weight unbalance bush which implements this invention. It is the II-II direction sectional drawing of FIG. It is a front view which shows the other example of the weight imbalance bush which implements this invention. FIG. 4 is a cross-sectional view in the IV-IV direction of FIG. 3. It is a front view which shows the further another example of the weight imbalance bush which implements this invention. FIG. 6 is a cross-sectional view in the VI-VI direction of FIG. 5. It is a front view which shows the further another example of the weight imbalance bush which implements this invention. It is a VIII-VIII direction sectional view of Drawing 7. It is a front view which shows the further another example of the weight imbalance bush which implements this invention. It is XX direction sectional drawing of FIG. It is the front view which showed typically the effect | action by the weight unbalance bush in this invention. It is a sectional side view which shows the whole structure of a turbocharger. It is a front view which shows an example of the conventional floating bush. It is the XIV-XIV direction sectional drawing of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Housing 6 Rotating shaft 8 Floating bush 10 Oil supply hole 10a, 10b Oil supply hole 10c, 10d Oil supply hole 10e, 10f Oil supply hole 10g, 10h Oil supply hole 11 Floating bush body 12 Weight unbalance bush 14 Weight adjustment hole 15 Large diameter part 16 Weight adjustment notch 18 Weight adjustment heterogeneous member 20 Oil film A Equal spacing B Unequal spacing

Claims (8)

  A floating bush bearing structure in which a cylindrical floating bush is disposed between the rotating shaft and the housing, and the rotating shaft is rotatably supported on the housing via an oil film formed on the inner and outer peripheral sides of the floating bush. A floating bush bearing structure, wherein the floating bush is constituted by a weight unbalance bush having a weight unbalance amount in a circumferential direction on a floating bush body.   2. The floating bush bearing structure according to claim 1, wherein the weight unbalance bush has a weight unbalance amount in a circumferential direction that does not contact the rotating shaft and the housing due to a centrifugal force generated by the rotation of the weight unbalance bush.   The weight unbalance bush has a weight unbalance amount in the circumferential direction by forming a lubrication hole in the floating bush main body that has a uniform bore and unequal spacing in the circumferential direction and penetrates in the radial direction. The floating bush bearing structure according to claim 1 or 2.   The weight unbalance bush has a weight unbalance amount in the circumferential direction by forming oil supply holes in the floating bush body at equal intervals in the circumferential direction and having unequal apertures and penetrating in the radial direction. The floating bush bearing structure according to claim 1 or 2.   The weight unbalance bush has a weight adjustment hole that penetrates or does not pass through the floating bush body in a floating bush body that has a uniform bore in the circumferential direction and has a uniform bore and that penetrates in the radial direction. The floating bush bearing structure according to claim 1 or 2, further comprising a weight unbalance amount in a circumferential direction.   The weight unbalance bush is a weight unbalance in the circumferential direction by forming a weight adjustment notch in the floating bush body with a uniform bore in the circumferential direction and an oil supply hole penetrating in the radial direction. The floating bush bearing structure according to claim 1, wherein the floating bush bearing structure is provided with an amount.   The weight unbalance bush is a weight unbalance amount in the circumferential direction by attaching a different weight adjusting member to the floating bush body that has a uniform bore in the circumferential direction and has an oil hole that penetrates in the radial direction. The floating bush bearing structure according to claim 1 or 2, further comprising: The floating bush bearing structure according to claim 1, wherein the floating bush bearing structure is applied to a turbocharger bearing structure.

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