JP2008106640A - Seal bushing assembling/disassembling device of turbine rotor for supercharger and seal bushing assembling/disassembling method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To certainly and easily perform assembling/disassembling of a seal part in a supercharger capable of only exchanging the seal part when the seal part is worn. <P>SOLUTION: In the seal bushing assembling/disassembling device of the turbine rotor for the supercharger, a seal bushing 42 is press-fitted and removed to a neck part 32 of a turbine shaft 41. The device is constituted by a bushing pushing cylinder fitted to the turbine shaft and capable of being abutted on an end surface of the seal bushing; a holder divided to a plurality of parts, externally fitted to the bushing pushing cylinder and capable of being fitted to grooves 34, 35 formed on the seal bushing; and a bind ring externally fitted to the holders and integrating the holders. The holder for retaining the seal bushing is guided to the turbine shaft through the bushing pushing cylinder at press-fitting and removal. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a turbo bush turbine rotor seal bush assembly, a disassembly device and a seal bush assembly for use in assembling or disassembling a detachable seal bush used in a turbocharger seal. It relates to a decomposition method.

  First, the outline of the supercharger will be described with reference to FIG.

  A turbine housing 2 and a compressor housing 3 are coaxially connected to both sides of the bearing housing 1, and a turbine shaft 4 is rotatably supported on the bearing housing 1 via a bearing 5. A turbine impeller 6 housed in the turbine housing 2 is fixed to the part, and a compressor impeller 7 is fixed to the other end of the turbine shaft 4.

  The turbine impeller 6 is made of a heat-resistant alloy because it rotates in high-temperature exhaust gas, the turbine shaft 4 is usually made of steel, and the turbine shaft 4 and the turbine impeller 6 are required means such as welding. And is configured as a turbine rotor 18.

  A bearing support portion 10 is formed inside the bearing housing 1, and the bearing 5 is fitted into the bearing support portion 10. The periphery of the bearing support portion 10 is a cavity 8, and an oil drain hole 9 communicating with the cavity 8 is formed in the lower portion of the bearing housing 1. A lubricating oil introduction hole 11 is formed in a required position of the bearing housing 1, an oil passage 12 and a through hole 13 are formed in the bearing support portion 10, and the oil passage 12 is formed in the lubricating oil introduction hole 11. The lubricating oil is communicated to the bearing 5, and the through hole 13 discharges the lubricating oil flowing out from the bearing 5 to the cavity 8.

  The lubricating oil introduction hole 11 communicates with a lubricating oil circulation circuit (not shown) of the engine, and the drain oil hole 9 is connected to an oil cooler (not shown) of the lubricating oil circulation circuit.

  A cooling water flow path 14 is formed along the joint surface of the bearing housing 1 with the turbine housing 2, and the cooling water flow path 14 communicates with an engine cooling water circulation circuit (not shown).

  The turbine housing 2 has a scroll passage 15 formed around the turbine impeller 6, and the scroll passage 15 communicates with the turbine impeller 6 through an annular gas passage 16. The turbine housing 2 is formed with an exhaust port 17 concentric with the turbine impeller 6 at the center.

  The compressor housing 3 includes a seal plate 24 concentrically fixed to the bearing housing 1 and a housing main body 25 concentrically fixed to the seal plate 24, and an annular passage 26 is provided around the compressor wheel 7. The structure is formed. A discharge hole (not shown) communicates with a required position of the annular passage 26, and the discharge hole (not shown) communicates with a combustion chamber side of an engine (not shown). A suction hole 23 concentric with the compressor wheel 7 is formed in the center of the housing body 25 so as to face the compressor wheel 7.

  Around the compressor wheel 7, a diffuser portion 28 communicating with the annular channel 26 is formed.

  Exhaust gas from an engine (not shown) passes through the scroll passage 15 and the annular gas passage 16, passes through the turbine impeller 6, and is discharged from the exhaust port 17. Then, the turbine impeller 6 is rotated.

  The rotation of the turbine impeller 6 causes the compressor impeller 7 to rotate through the turbine shaft 4, and combustion air is sucked from the suction hole 23. The sucked combustion air is absorbed by the compressor impeller 7. It is compressed by passing through the rotation and the diffuser portion 28, and flows into the annular channel 26. The compressed air is supplied from the annular passage 26 to the engine (not shown) through the discharge hole (not shown).

  Lubricating oil is supplied to the bearing 5 from the lubricating oil introduction hole 11, lubricates the rotating portion of the turbine shaft 4, and is discharged through the through hole 13, the cavity 8, and the oil draining hole 9. The lubricating oil lubricates the rotating part of the shaft and also cools the turbine shaft 4 and the bearing 5. The exhaust gas flowing through the turbine housing 2 has a high temperature, and the cooling water flowing through the cooling water flow path 14 prevents the temperature of the bearing housing 1 from becoming too high due to the heat transmitted from the turbine housing 2. The joint portion of the turbine housing 2 of the bearing housing 1 is cooled.

  Further, a seal portion 31 for shutting off the inside of the turbine housing 2 through which high-temperature exhaust gas flows and the cavity 8 cooled by the lubricating oil and the cooling water is provided in the turbine housing 2 of the bearing housing 1. It is provided in the boundary part.

  The seal part 31 will be described.

  The seal portion 31 is constituted by a neck portion 32 of the turbine shaft 4 and a hole 33 of the bearing housing 1 through which the neck portion 32 passes.

  The neck portion 32 is formed with two grooves 34 and 35 and bank portions 36 and 37 adjacent to the grooves 34 and 35, and a C-shaped seal ring 38 is formed in the groove 34 on the turbine impeller 6 side. The seal ring 38 is slidably fitted, and is fixed to the bearing housing 1 by an expansion force due to elasticity. Therefore, the inside of the turbine housing 2 and the inside of the bearing housing 1 are blocked by the seal ring 38.

  Further, the other groove 35 performs oil drainage by the interaction with the bank portion 37 so that the lubricating oil supplied to the bearing 5 does not enter the turbine housing 2 side.

  When the supercharger is used in a marine engine, the exhaust gas is hot, and the heat reacts with the lubricating oil to produce a very hard substance. Unburned material enters and accumulates in the gaps of the seal portion 31, and wears the seal ring 38, the groove 34, the bank portion 36, and the like of the neck portion 32.

  The gap increases due to wear of the seal ring 38, the groove 34, and the bank portion 36, and high-temperature exhaust gas enters the cavity 8, so that the lubricating oil is transformed into a hard foreign substance. For this reason, there is a possibility that the wear of the seal portion 31 is lost due to further progress of wear due to unburned materials and foreign matters.

  For this reason, it is desired to improve the wear resistance by curing the neck portion 32, but it is difficult to cure the neck portion 32 in a state where the turbine impeller 6 and the turbine shaft 4 are integrated. It is.

  Further, even when the groove 34 is partially worn, the turbine shaft 4 and the turbine impeller 6 must be exchanged when the turbine shaft 4 and the turbine impeller 6 are integrated.

  In addition, as a manufacturing method of a turbine rotor, there exists what is shown by patent document 1, and patent document 1 is a method of connecting a ceramic turbine rotor and a metal rotor shaft via a metal cylinder. It is shown.

Japanese Patent Laid-Open No. 3-210026

  In view of such circumstances, the present invention provides a turbocharger that can assemble and disassemble the seal part reliably and easily in a supercharger that can replace only the seal part when the seal part is worn. The present invention provides a method for assembling and disassembling a seal bush of a turbine rotor for a machine and a method of assembling and disassembling a seal bush of a turbine rotor for a turbocharger.

  According to the present invention, in a turbo bush turbine rotor seal bushing assembly / disassembly device in which a seal bush is press-fitted into and removed from a neck portion of a turbine shaft, the turbine bush is fitted to the turbine shaft and abuts against the end surface of the seal bush. A bush push cylinder that can be contacted, a holder that is fitted into the bush push cylinder and that can be fitted into a groove formed in the seal bush, and a holder that is fitted into the holder, and that fits together. Assembling and disassembling a seal bush of a turbo rotor for a turbocharger, which is configured to guide the holder holding the seal bush at the time of press-fitting and withdrawal with the turbine shaft through the bush push cylinder It concerns the device.

  Further, according to the present invention, in the turbo bush turbine rotor seal bushing assembly / disassembly device for press-fitting and removing the seal bush into and from the neck portion of the turbine shaft, the turbine bush is fitted to the end surface of the seal bush. A bush-pushing cylinder that can be contacted, a holder that is fitted into the bushing-pushing cylinder and that can be fitted into a groove formed in the seal bushing, and a holder that is fitted into the holder, and that fits together. The seal bush is press-fitted into one of the holder and the bush push cylinder when the seal bush is press-fitted to press-fit the seal bush, and when the seal bush is removed, the turbine is inserted into the holder. Assembling and disassembling the seal bush of the turbo rotor for the turbocharger, which applies a pushing force to the shaft and removes the seal bush from the turbine shaft It relates to.

  Furthermore, the present invention relates to a method of assembling and disassembling a seal bush of a turbo rotor for a turbocharger that heats the seal bush or cools the turbine shaft when the seal bush is press-fitted or removed. is there.

  According to the present invention, in a turbo bush turbine rotor seal bushing assembly / disassembly device for press-fitting / removing a seal bush to / from a neck portion of a turbine shaft, the end face of the seal bush is fitted to the turbine shaft. A bush-pushing cylinder that can be in contact with the bushing, a holder that is fitted into the bushing-pushing cylinder and that can be fitted into a groove formed in the seal bushing, and is fitted into the holder. It is composed of an integral bind ring, and the holder that holds the seal bush at the time of press-fitting and withdrawing is guided to the turbine shaft through the bush push cylinder, so that it is delicate at the time of press-fitting and withdrawing the seal bush. This eliminates the need for center alignment, prevents damage to the seal bush and the turbine shaft, and improves the workability of assembly and disassembly of the seal bush.

  Further, according to the present invention, in the turbo bush turbine rotor seal bushing assembly / disassembly device for press-fitting / removing the seal bush to / from the neck portion of the turbine shaft, the turbine bush is fitted to the turbine shaft, A bush push cylinder capable of contacting the end face, a plurality of divided holders fitted to the bush push cylinder and fitted in a groove formed in the seal bush, and fitted to the holder; the holder The seal bush is press-fitted into one of the holder and the bush push cylinder when the seal bush is press-fitted, and the seal bush is press-fitted. On the other hand, a pushing force is applied to the turbine shaft to remove the seal bush from the turbine shaft. The bush push cylinder and the flanged holder are held so as to be concentric with the turbine shaft, and because no external force is applied directly to the seal bush for press-fitting and withdrawal, damage to the seal bush and the turbine shaft is prevented. In addition, excellent effects such as improvement of workability of assembly and disassembly of the seal bush are exhibited.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

  First, referring to FIGS. 1 and 2, a turbo rotor 40 for a supercharger in which the present invention is implemented will be described.

  The turbine rotor 40 and the turbocharger turbine rotor 18 shown in FIG. 4 are equivalent, and in FIG. 1 and FIG. Further, the turbine rotor 40 according to the present invention can be manufactured so as to be compatible with the turbine rotor 18 of the supercharger.

  The turbine impeller 6 is made of a heat-resistant alloy, for example, Inconel (registered trademark) which is a nickel heat-resistant alloy, and one end (hereinafter referred to as a lower end) of a steel turbine shaft 41 is welded to the turbine impeller 6.

  A seal bush 42 is press-fitted into the neck portion 32 of the turbine shaft 41, and a groove 34 is formed between the bank portion 43 and the bank portion 36 in the seal bush 42, and the bank portion 36 and the bank portion 37 are formed. A groove 35 is formed between the two. The groove 34 is fitted with a seal ring 38 (see FIG. 4), and the groove 35 and the bank portion 37 constitute an oil drain.

  Thus, the turbine shaft 41 has the same specifications as the conventional turbine shaft 4 in a state where the seal bush 42 is press-fitted.

  The seal bush 42 is fixed to the turbine shaft 41 by a fastening force by press fitting. The turbine shaft 41 can be pulled out by applying a pulling force greater than the fastening force to the seal bush 42. That is, the seal bush 42 can be replaced with the turbine shaft 41.

  In addition, the replacement of the seal bush 42 reduces the maintenance cost. However, by subjecting the seal bush 42 to the curing process, the replacement period becomes longer and the maintenance cost is further reduced.

  The material of the seal bush 42 is, for example, SACM, carbon steel material (S material), manganese steel material (SMn material), manganese chromium steel material (SMnC material), chromium steel material (SCr material), chromium molybdenum steel. Steel material (SCM material), nickel chrome steel material (SN material), nickel chrome molybdenum steel material (SNCM material), tool steel material (SKH material), titanium alloy (Ti-Al-V), etc. are selected, and the seal The bush 42 is subjected to wear resistance treatment.

  As the wear resistance treatment, as a treatment for reducing the friction coefficient, a layer having a solid lubricating material is formed on the surface of the groove 34 and the seal ring 38 by a method such as plating. Examples of the material having solid lubricity include graphite, nickel, molybdenum and the like, and those having a layer hardness of Hv500 also function as a curing process.

  By subjecting the seal ring 38 and the seal bush 42 to surface treatment with a material having solid lubricity, the life of the seal ring 38 and the groove 34 is extended. For example, it is possible to extend the life by about 19 times in the wear resistance treatment with graphite having solid lubricity, and about 4 times in the wear resistance treatment containing nickel or molybdenum.

  As the anti-abrasion treatment, the surface is hardened. As the curing treatment, surface hardening that diffuses and permeates metals such as Al, Cr, Ti, W and their carbides from the material surface, thermal spraying with chromium carbide, tungsten carbide, physical vapor deposition or chemical vapor deposition of materials including ceramics, Any one of platings containing nickel, boron and phosphorus or superposition is processed so as to obtain a hardness of at least Hv 500 or more.

  Further, the wear resistance treatment and the hardening treatment may be applied to the inner cylindrical surface of the seal bush 42 and the tip portion of the turbine shaft 41 including the fitting portion of the bush. The fatigue strength of the neck portion 32 of the turbine shaft 41 is increased by subjecting the inner cylindrical surface of the seal bush 42 and the tip of the turbine shaft 41 to wear resistance and hardening.

  Next, a seal bush assembly and disassembly device for press-fitting and removing the seal bush 42 will be described with reference to FIG.

  The shaft diameter of the turbine shaft 41 gradually decreases in a direction away from the turbine impeller 6 (upward in FIG. 3), and the neck portion 32 to which the turbine shaft 41 is fitted is the thickest. Next, the part (bearing fitting part 45) in which the bearing 5 is fitted is thickened. A bush push tube 46 is slidably fitted to the bearing fitting portion 45, and the bush push tube 46 is fitted to a flanged holder 47.

  The flanged holder 47 is a plane including an axial center and is divided into two halves 47a. On the inner surface of the lower end portion of the flanged holder 47 (the end portion on the turbine impeller 6 side), protrusions 48 and 49 are provided. , And the protrusions 48 and 49 can be fitted into the grooves 34 and 35. Accordingly, when the seal bush 42 is sandwiched between the split bodies 47a and 47a, the protrusions 48 and 49 are fitted into the grooves 34 and 35.

  The flanged holder 47 is formed with a flange 51 perpendicular to the axis, a long cylindrical portion 52 is formed above the flange 51, and a short cylindrical portion 53 is formed below the flange 51. Yes. A bind ring 54 can be attached to and detached from the long cylindrical portion 52, and the integral state of the holder 47 with flange is maintained by fitting the bind ring 54 to the long cylindrical portion 52. ing.

  The short cylindrical portion 53 can be fitted into the holding hole 56 of the base plate 55, and the base plate 55 is divided into two by a plane including the center of the holding hole 56. Although not shown, the base plate 55 includes a fixture for maintaining an integrated state.

  As described above, the shaft diameter of the turbine shaft 41 is gradually reduced upward, and a step is formed at a location where the diameter changes. A shaft pushing cylinder 57 is detachably fitted to a portion having a smaller diameter than the bearing fitting portion 45, and the lower end of the shaft pushing cylinder 57 is in contact with the step.

  Hereinafter, the press-fitting and withdrawal of the turbine shaft 41 using the seal bushing assembly and disassembling apparatus will be described.

  When press-fitting the turbine shaft 41, the base plate 55 may not be used.

  The turbine rotor 40 is made to stand upright with the turbine impeller 6 down.

  In a state where the seal bush 42 is held and held by the holder 47 with flange, the bind ring 54 is fitted to the long cylindrical portion 52. The bush push tube 46 is fitted into the long tube portion 52. When the bush push tube 46 is completely inserted and the lower end is in contact with the seal bush 42, the upper end of the bush push tube 46 is slightly protruded from the long tube portion 52.

  The seal bush 42 is held at the lower end of the flanged holder 47. That is, the seal bush 42 is held by the seal bush assembly and disassembly device. The shaft pushing cylinder 57 may not be used.

  The turbine shaft 41 is inserted into the bush push tube 46. Since the diameter of the turbine shaft 41 is gradually changed toward the turbine impeller 6, the bush push tube 46 is easily fitted to the bearing fitting portion 45. Further, the seal bush 42 has sufficient play with respect to the bearing fitting portion 45, and the bearing fitting portion 45 smoothly passes through the seal bush 42.

  The bush push tube 46 is guided by the bearing fitting portion 45, and the long tube portion 52 is guided by the bearing fitting portion 45 through the bush push tube 46 and held by the bush push tube 46. The seal bush 42 is aligned with the neck portion 32 through the bush push tube 46.

  The press-fitting of the seal bush 42 into the neck portion 32 causes a pushing force to act on the upper end of the bush push tube 46. Since the bush push tube 46 transmits a pushing force to the upper end surface of the seal bush 42, the bush pushing cylinder 46 can be press-fitted without applying a load to the bank portions 36, 37, 43 which are weak in strength.

  When the bank portions 36, 37, 43 have sufficient strength, a pushing force may be applied to the long tube portion 52.

  Further, depending on the environment in which the turbine rotor 40 is used, the friction force between the inner cylindrical surface of the seal bush 42 and the surface of the bush fitting portion of the turbine shaft 41 is increased, and the seal bush 42 In order to prevent the turbine shaft 41 from being displaced, it is necessary to make the diameter of the bush fitting portion of the turbine shaft 41 relatively larger than the diameter of the inner cylinder of the seal bush 42, that is, to make a tightening allowance larger. is there.

  In such a case, it is necessary to relatively increase the pushing force applied to the upper end of the bush push tube 46, and a required load acts on the bank portions 36, 37, and 43. Therefore, at the time of press-fitting, the seal bush 42 is heated to increase the diameter of the inner cylinder of the seal bush 42, or the turbine shaft 41 is cooled to reduce the diameter of the bush fitting portion of the turbine shaft 41. By shrinking, the press-in can be performed without applying a large load to the bank portions 36, 37, and 43.

  When the press-fitting is completed, the bind ring 54 is removed, the long tube portion 52 is divided, and the bush push tube 46 is pulled out.

  Next, the case where the seal bush 42 is removed will be described.

  The bush push tube 46 is fitted into the bearing fitting portion 45, and the flanged holder 47 is attached to the bush push tube 46. In this state, the lower end portion of the bush push tube 46 is fitted in the grooves 34 and 35. The neck portion 32 is fitted into the bush pushing cylinder 46, and the shaft pushing cylinder 57 is fitted into the upper portion of the turbine shaft 41.

  From the state in which the base plate 55 is divided, the short cylindrical portion 53 is sandwiched with the holding hole 56, and the base plate 55 is integrated by a fixture. The base plate 55 is supported at a required height by a leg base (not shown). The seal bushing assembly and disassembly device is in a state of being erected on the base plate 55 through the flange 51.

  When a pushing force is applied to the upper end of the shaft pushing cylinder 57, a downward force is applied to the turbine shaft 41. The grooves 34, 35 and the protrusions 48, 49 are fitted, and the seal bush 42 is held by the holder 47 with flange through the grooves 34, 35, the protrusions 48, 49, and The flanged holder 47 is restrained from being displaced downward by the base plate 55 via the flange 51. Therefore, when the pushing force becomes larger than the fastening force by press-fitting, the seal bush 42 is left and the turbine shaft is left. Only 41 moves downward, and the seal bush 42 is detached from the neck portion 32.

  If there is no possibility of damaging the upper end portion of the turbine shaft 41, the pushing cylinder 57 may be omitted, and a pushing force may be applied directly to the upper end of the turbine shaft 41.

  Further, the allowance between the inner cylinder surface of the seal bush 42 and the bush fitting portion of the turbine shaft 41 is large, and the frictional force between the inner cylinder surface of the seal bush 42 and the surface of the bush fitting portion of the turbine shaft 41 is large. In the case of a large turbine rotor, the seal bush 42 may be locally heated or the turbine shaft 41 may be cooled during removal.

  By removing the flanged holder 47 from the base plate 55, removing the bind ring 54 and dividing the flanged holder 47, the removed seal bushing 42 can be easily removed from the seal bushing assembly and disassembly device. .

  As described above, the seal bush 42 is press-fitted and withdrawn in the state of being aligned with the turbine shaft 41, and further, no external force for press-fitting and withdrawing is directly applied to the seal bush 42. By press-fitting and removing the bush 42, damage to the turbine shaft 41 and damage to the seal bush 42 are prevented.

  In addition, since a fine alignment work is not required, the work becomes easy and skill is not required.

  The bush push tube 46 may be divided into three parts. Similarly, the base plate 55 may be divided into three parts. The flange 51 may be provided at the upper end portion of the long cylindrical portion 52, or the flange 51 is omitted, and the holding hole 56 into which the short cylindrical portion 53 is fitted is a stepped hole. You may make it restrain the downward displacement of the cylinder part 53. FIG.

It is a side view which shows an example of the turbine rotor by which this invention is implemented. It is the A section enlarged view of FIG. It is sectional drawing which shows embodiment of this invention. It is sectional drawing which shows an example of the supercharger in which a turbine rotor is used.

Explanation of symbols

4 Turbine shaft 6 Turbine wheel 32 Neck portion 34 Groove 35 Groove 40 Turbine rotor 41 Turbine shaft 42 Seal bush 45 Bearing fitting portion 46 Bush push tube 47 Holder with flange 51 Flange 52 Long tube portion 55 Base plate

Claims (3)

  A bushing that can be fitted to the turbine shaft and abutted against the end face of the seal bush in a turbocharger turbine rotor seal assembly and disassembly device that press-fits and removes the seal bush to and from the neck portion of the turbine shaft A push cylinder, a holder that is fitted into the bush push cylinder and that can be fitted into a groove formed in the seal bush, and a bind ring that fits into the holder and integrates the holder Assembling the seal bush of the turbo rotor for a turbocharger, wherein the holder for holding the seal bush at the time of press-fitting and withdrawing is guided to the turbine shaft via the bush push cylinder, Disassembly equipment.   A bushing that can be fitted to the turbine shaft and abutted against the end face of the seal bush in a turbocharger turbine rotor seal assembly and disassembly device that press-fits and removes the seal bush to and from the neck portion of the turbine shaft A push cylinder, a holder that is fitted into the bush push cylinder and that can be fitted into a groove formed in the seal bush, and a bind ring that fits into the holder and integrates the holder When the seal bush is press-fitted, a pressing force is applied to one of the holder and the bush push cylinder to press-fit the seal bush, and when the seal bush is removed, the force is applied to the holder against the turbine shaft. Assembling the seal bush of the turbine rotor for a turbocharger, wherein the seal bush is removed from the turbine shaft by acting Decomposition method.   3. The turbo bush turbine seal bush assembly and disassembly method according to claim 2, wherein the seal bush is heated or the turbine shaft is cooled when the seal bush is press-fitted or when the seal bush is removed.

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