JP2008184948A - Turbocharger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbocharger capable of improving efficiency of supercharging, reducing manufacturing cost, and preventing the oil flowing out of a bearing part from leaking onto an impeller side. <P>SOLUTION: This turbocharger is constituted by arranging an oil thrower 36 between the bearing part 31 supporting a turbine shaft 5 in a bearing housing 3 and an impeller 6 in front of it and forming an oil drip facing part 39 provided integrally with the bearing housing 3 to position a seal plate 44 facing the outer periphery of a front part of the oil thrower 36 to prevent oil from leaking from the bearing part 31 onto the impeller 6 side on a rear surface of the impeller 6 and facing the outer periphery of a rear part of the oil thrower 36 to constitute an oil sump 40 in the bearing housing 3. The seal plate 44 is constituted by a press-fitting plate 47, and diameter of the press-fitting plate 47 is set to be smaller than outside diameter of the impeller 6 and be equal to the minimum bore for work for working the outer periphery 42 of the oil thrower facing part 39 or working an oil discharge hole 41 provided in the oil drip facing part 39 or more. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a turbocharger configured to prevent lubricating oil from a bearing portion from leaking to an impeller side.

  In general, a turbocharger has a bearing housing 3 integrally disposed between a turbine housing 1 and a compressor housing 2 as shown in FIGS. 9 and 10, and a turbine shaft 5 is connected to the bearing housing 3 via a bearing portion 4. It is supported rotatably. One (front side) of the turbine shaft 5 is provided with an impeller 6 surrounded by the compressor housing 2, and the other (rear side) of the turbine shaft 5 is provided with a turbine rotor 7 surrounded by the turbine housing 1. It has been.

  The bearing portion 4 disposed inside the bearing housing 3 regulates the floating bush 4a as a rotary bearing disposed at intervals in the axial direction of the turbine shaft 5 and the movement of the floating bush 4a in the axial direction. An inner plate 4b, an outer thrust receiver 4c fixed in the bearing housing 3 via bolts 8, and a thrust collar disposed between the inner plate 4b and the outer thrust receiver 4c and contacting the step portion 5a of the turbine shaft 5. It is comprised by the thrust bearing which consists of 4d.

  The bearing housing 3 is provided with a supply hole 9 formed in the axial direction of the turbine shaft 5 and a first branch flow path 10 branched from the supply hole 9 toward the floating bush 4a. The lubricating oil supplied to the supply hole 9 is supplied from the first branch flow path 10 between the floating bush 4a and the bearing housing 3 and between the floating bush 4a and the turbine shaft 5 to form an oil film, thereby forming a turbine shaft. 5 rotations are supported. Here, the floating bush 4 a is provided with an oil passage 11 penetrating in the radial direction in order to form an oil film between the floating bush 4 a and the turbine shaft 5.

  Further, the bearing housing 3 is formed with a second branch flow path 12 branched separately from the supply hole 9, and the lubricating oil supplied to the supply hole 9 is formed from the second branch flow path 12 to the outer thrust receiver 4c. Through the oil passage 13, the oil is supplied between the outer thrust receiver 4c and the thrust collar 4d to form an oil film and receive a thrust load.

  On the other hand, a cylindrical oil drain 14 is provided between the thrust collar 4 d of the bearing portion 4 and the impeller 6 on the outer periphery of the turbine shaft 5. An annular groove 14b is formed on the outer peripheral surface of the front portion 14a of the oil drain 14, and a piston ring-shaped seal ring 15 is disposed in the groove 14b. The rear portion 14c of the oil drain 14 is fitted with a slight gap 16 on the inner peripheral surface of the outer thrust receiver 4c.

  A seal plate 18 fixed to the bearing housing 3 via bolts 17 is disposed at a position facing the outer periphery of the front portion 14a of the oil drill 14 and the oil drill is disposed on the inner peripheral end surface of the seal plate 18. The piston ring-shaped seal ring 15 disposed in the 14 grooves 14b is in contact with the spring force to spread. The seal plate 18 is located on the back surface of the impeller 6 and is formed larger than the outer diameter of the impeller 6, and part of the flow path 20 of the diffuser portion 19 for rectifying the compressed air from the compressor. Forming.

  When driving such a turbocharger, the turbine rotor 7 is rotated by engine exhaust gas or the like, and the impeller 6 is driven by the rotation of the turbine shaft 5 to suck and compress air from the intake port 21. The compressed air is rectified by the flow path 20 of the diffuser unit 19 and is supercharged to the downstream engine so as to improve the output performance of the engine (see, for example, Patent Document 1).

At this time, in the bearing portion 4, when lubricating oil is supplied from the supply hole 9, an oil film is formed between the floating bush 4a and the bearing housing 3, and between the floating bush 4a and the turbine shaft 5, thereby forming an oil film. The lubricating oil thus discharged flows out of the gap between the inner plate 4b and the turbine shaft 5, and the gap between the inner plate 4b and the thrust collar 4d. On the other hand, the lubricating oil is also supplied between the outer thrust receiver 4c and the thrust collar 4d to form an oil film, and the lubricating oil that has formed the oil film is a gap between the rear portion 14c of the oil cutter 14 and the outer thrust receiver 4c. 16 is discharged.
JP 2002-38966 A

  However, in the turbocharger, when the separate seal plate 18 is assembled to the bearing housing 3 as in the conventional example, the unevenness 22 due to the bolt head portion 17a of the bolt 17 or the seal plate 18 is formed in the flow path 20 of the diffuser portion 19. Therefore, there is a problem that the supercharging efficiency is lowered by disturbing the air flow. Further, when assembling the seal plate 18, there is a possibility that scratches due to tools or the like may occur in the flow path 20 of the diffuser portion 19 where air is supercharged from the impeller 6. However, the air flow is disturbed and the supercharging efficiency is lowered. Further, the machining cost increases due to the threading of the bearing housing 3 and the like, and the number of parts such as bolts 17 used when the seal plate 18 is assembled increases, resulting in an increase in manufacturing cost.

  Further, it is preferable that the lubricating oil flowing out from the gap 16 between the rear portion 14c of the oil cutter 14 and the outer thrust receiver 4c flows out from the space 24 between the outer thrust receiver 4c and the seal plate 18. Since the turbine shaft 5 and the oil cutter 14 are rotating at high speed, the lubricating oil becomes mist and accumulates around the outer thrust receiver 4c, and this mist is transmitted to the seal ring 15 from the seal ring 15 to the impeller 6 side. There was a problem of leaking.

  The present invention has been made in view of such a situation, and is intended to improve turbocharging efficiency, reduce manufacturing cost, and further provide a turbocharger that prevents oil flowing out from a bearing portion from leaking to the impeller side. It is intended to provide.

  In the present invention, oil is disposed between a bearing portion that supports the turbine shaft on the bearing housing and the front impeller, and oil leakage from the bearing portion to the impeller side is prevented against the outer periphery of the front portion of the oil scrap. The seal plate is integrally provided with the bearing housing so as to be positioned on the back surface of the impeller, and further, the turbocharger is formed with an oil-cuttering confronting part formed on the bearing housing so as to constitute an oil sump facing the outer periphery of the rear part of the oil-drilling It is a charger, the seal plate is constituted by a press-fit plate, the press-fit plate has a diameter smaller than the outer diameter of the impeller, and the outer periphery of the oil-cuttered counter part is processed or provided in the oil-cage counter part The present invention relates to a turbocharger characterized by being equal to or greater than the minimum working diameter for processing the oil discharge hole.

  Further, in the present invention, an oil sump is formed at the first projecting portion projecting to the outer periphery at the rear end side of the oil drill, the second projecting portion projecting to the outer periphery at the midway position in the axial direction, and the oil drill facing portion. It is preferable to include a first pair of hooks that are opposed to the first protrusion and a second pair of hooks that are formed in the oil drilling hook and face the second protrusion.

  As described above, according to the turbocharger of the present invention, the seal plate is constituted by the press-fit plate and integrated with the bearing housing. Therefore, the bolt head is not required to be fixed, the unevenness due to the bolt head portion is eliminated, and the diameter of the press-fit plate is reduced. Since the outer diameter of the impeller is smaller than the outer diameter of the impeller, unevenness due to the boundary portion of the press-fitting plate can be positioned on the back surface of the impeller different from the flow path of the diffuser portion, thus preventing air from being disturbed by the unevenness, A decrease in supercharging efficiency can be prevented. Even if a scratch is generated by a tool or the like when press-fitting the press-fitting plate, the scratch can be positioned on the back surface of the impeller different from the flow path of the diffuser part. It is possible to prevent air from being disturbed and to prevent a reduction in supercharging efficiency. Furthermore, since the seal plate is formed of a press-fit plate, the processing cost is reduced by eliminating the need for screwing to fix the bearing housing, etc., and the number of parts is reduced by eliminating the need for bolt assembly. Cost is reduced.

  In addition, the oil reservoir and the oil drainage counter part constitute an oil sump, and the lubricating oil flowing out from the bearing part flows into the oil sump and is discharged to the outside through the oil discharge hole. The amount of lubricating oil leaking from between the parts to the impeller side can be reduced as much as possible. Furthermore, since the diameter of the hole provided in the seal plate into which the press-fitting plate is press-fitted is a diameter that can process the outer periphery of the oil-cuttered counter part, the outer periphery of the oil-cuttered counter part is appropriately formed, and the oil and oil By flowing the lubricating oil that has oozed from between the cut-out counter part along the outer periphery of the oil-exposed part, it is possible to prevent the lubricating oil from going to the seal plate and to prevent leakage to the impeller side. Furthermore, the diameter of the hole provided in the seal plate and into which the press-fitting plate is press-fitted is such that the oil discharge hole can be machined in the oil-cuttered counter part, so that the lubricating oil flowing into the oil sump from the bearing part can be The oil can be immediately discharged to the outside from the discharge hole, so that the lubricating oil can be prevented from moving toward the seal plate, and the lubricating oil can be prevented from leaking to the impeller side.

  In the present invention, an oil sump is formed at the first projecting part projecting to the outer periphery at the rear end side of the oil drill, the second projecting part projecting to the outer periphery at an axially halfway position, and the oil drilling counter part. An oil sump can be easily formed by configuring the first pair of flanges facing the first projecting portion and the second pair of flanges formed on the oil drilled facing portion and facing the second projecting portion.

  According to the turbocharger of the present invention, it is possible to improve the supercharging efficiency and reduce the manufacturing cost by the configuration of the seal plate provided with the press-fitting plate. Further, the turbocharger is provided between the oil drill and the oil drill counter part. The oil sump configuration allows the lubricating oil that has flowed out of the bearing portion to be immediately discharged to the outside through the oil discharge hole, so that the lubricating oil can be prevented from leaking to the impeller side. Can play.

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

  FIGS. 1 to 8 show embodiments of the present invention. The parts denoted by the same reference numerals as those in FIGS. 9 and 10 represent the same components, and the turbocharger according to the embodiment of the present invention is a conventional one. In order to solve the problem caused by the discharge of the lubricating oil from the bearing portion 4, the following configuration is adopted.

  The bearing portion 31 shown in FIGS. 1 and 2 that supports the turbine shaft 5 inside the bearing housing 3 includes a floating bush 32 having an integral structure that supports the turbine shaft 5 at two points. Lubricating oil is supplied to the floating bush 32 by a supply hole 33 formed in the bearing housing 3 and a flow path 34 extending from the supply hole 33, and between the floating bush 32 and the bearing housing 3 and the floating bush 32. An oil film is formed between the bush 32 and the turbine shaft 5 to support the rotation of the turbine shaft 5. Here, the floating bush 32 is provided with an oil passage 35 penetrating in the radial direction in order to form an oil film between the floating bush 32 and the turbine shaft 5.

  One (front side) of the floating bush 32 of the bearing portion 31 is provided with an oil drain 36 that also serves as a thrust bearing of the turbine shaft 5 and is positioned between the floating bush 32 and the front impeller 6 on the outer periphery of the turbine shaft 5. It has been. An annular groove 36b is formed on the outer peripheral surface of the front portion 36a of the oil drill 36, and a piston ring-shaped seal ring 37 is disposed in the groove 36b. In addition, on the outer periphery of the rear portion 36 c of the oil drill 36, a cylindrical oil drill counter extending from the inner peripheral portion 38 of the bearing housing 3 that supports the bearing portion 31 to the front side along the axial direction of the turbine shaft 5. A portion 39 is formed.

  An oil sump 40 is formed between the rear portion 36 c of the oil drain 36 and the oil draining counter part 39. The oil sump 40 is formed in a first projecting portion 36d projecting to the outer periphery at the end of the rear portion 36c of the oil drill 36, a second projecting portion 36e projecting to the outer periphery in the midway position in the axial direction, and an oil drill counter part 39. A first pair of flanges 39a facing the first protrusion 36d, and a second pair of flanges 39b formed on the oil draining counterpart 39 and facing the second protrusion 36e, the first protrusion 36d and the second It is comprised by the groove | channel 40a located between the protrusion parts 36e, and the groove | channel 40b located between the 1st pair collar part 39a and the 2nd pair collar part 39b. Further, the oil sump 40 is provided with a plurality of oil discharge holes 41 penetrating from the groove 40b to the outer periphery of the oil catching portion 39, and the oil discharge holes 41 are directed outward from the groove 40b. It is formed obliquely so as to extend in a direction away from the side.

  Here, the outer periphery 42 of the front end portion of the oil-clogging confronting portion 39 is processed in two steps by the processing tool 43 shown in FIG. 5 to ensure the wall thickness and at the same time rearward from the inner periphery to the outer periphery. So that the lubricating oil flows outwardly away from the impeller 6 along the outer periphery 42 of the counterbore 39.

  When the floating bush 32 of the bearing portion 31 is lubricated, the lubricating oil flows out between the floating bush 32 and the bearing housing 3 and between the floating bush 32 and the turbine shaft 5 as in the conventional bearing portion 4. The lubricating oil that has flowed out flows into the oil sump 40 from between the first projecting portion 36d of the oil drill 36 and the first pair of flange portions 39a of the oil drill counter flange portion 39, and temporarily accumulates. It is discharged in the direction of separating. As a result, the amount of lubricating oil that oozes out between the second protrusion 36e of the oil drill 36 and the second counter part 39b of the oil counter part 39 as the turbine shaft 5 and the oil part 36 rotate at a high speed is reduced. In addition, the lubricating oil that has oozed out flows in a direction away from the impeller 6 along the outer periphery 42 of the counterbore 39 and prevents the lubricating oil from moving toward the impeller 6 as a whole.

  On the other hand, the turbocharger of the present invention is further configured as follows in order to solve the problem caused by the conventional seal plate 18 being separate from the bearing housing 3.

  A seal plate 44 that is located on the back surface of the impeller 6 and is integrated with the bearing housing 3 is provided at a position facing the outer periphery of the front portion 36 a of the oil drain 36. The seal plate 44 is formed integrally with the bearing housing 3 and extended to a required position on the back surface of the impeller 6, and a press-fit plate that is tightly press-fitted into the inner peripheral hole 46 of the fixed seal plate 45. 47. Further, a seal ring 37 disposed in the groove 36b of the oil drill 36 is in contact with the inner peripheral end surface of the press-fitting plate 47 by a spring force for spreading.

  Here, the outer diameter of the press-fit plate 47 is smaller than the outer diameter of the impeller 6, and the processing tool 43 passes through the hole 46 of the fixed seal plate 45 to process the outer periphery 42 of the oil drilling counter part 39 or the oil discharge hole 41. It is formed in a size equal to or greater than the minimum working diameter required for processing the workpiece. The outer diameter of the press-fitting plate 47 in FIGS. 1 and 2 is the same diameter as the outer diameter of the oil drilling flange 39 or slightly larger than the outer diameter of the oil drilling flange 39 (same diameter or larger). If the hole 46 has a large diameter, the processing tool 43 can easily process the outer periphery 42 and the oil discharge hole 41 of the oil drilling confronting portion 39, but the diameter of the press-fit plate 47 is also increased and press-fitted. Since there is a problem that the working force becomes large, it is preferable that the diameters of the hole 46 and the press-fit plate 47 are small.

  When press-fitting the press-fit plate 47 into the hole 46 of the fixed seal plate 45, first, as shown in FIG. 6, the oil drain 36 is disposed on the inner peripheral end surface of the press-fit plate 47 via the seal ring 37, and then As shown in FIG. 7, the bearing housing 3 is placed on the pedestal 48 so that the compressor side faces upward, and the press-fitting plate 47 with the oil drain 36 is temporarily placed so as to match the hole 46 of the fixed seal plate 45, and FIG. It press-fits with a press (not shown) using the press-fitting jig 49 shown. As a result, the first projecting portion 36d and the second projecting portion 36e of the oil drill 36 are aligned with the first pair of flange portions 39a and the second counter flange portion 39b of the bearing housing 3, and between the fixed seal plate 45 of the bearing housing 3 ( It is arranged so that no step occurs at the boundary portion. Here, reference numeral 50 in FIG. 8 denotes a press receiver that protrudes to the outer periphery so as to apply a pressing force to a press-fitting jig 49 into which the seal plate 44 is press-fitted.

  After the press-fit plate 47 and the oil drain 36 are disposed in the bearing housing 3, the turbine shaft 5, the impeller 6, the turbine rotor 7, the turbine housing 1, the compressor housing 2, and the like are assembled to constitute the whole. At the time of driving, the turbine rotor 7 is rotated by engine exhaust gas or the like to drive the impeller 6 connected to the turbine shaft 5. The impeller 6 sucks and compresses air from the intake port 21, and the compressed air is The air is rectified in the flow path 20 of the diffuser unit 19 and is supercharged to the downstream engine.

  As described above, according to the turbocharger of the embodiment of the present invention, the press-fitting plate 47 is press-fitted into the fixed seal plate 45 and integrated with the bearing housing 3. Since the diameter of the press-fit plate 47 is made smaller than the outer diameter of the impeller 6, the unevenness due to the boundary portion of the press-fit plate 47 is positioned on the back surface of the impeller 6 different from the flow path 20 of the diffuser portion 19. Therefore, it is possible to prevent the air from being disturbed by the unevenness and prevent the supercharging efficiency from being lowered. Further, even when a scratch is generated by a tool such as the press-fitting jig 49 when the press-fitting plate 47 is press-fitted, the flaw can be positioned on the back surface of the impeller 6 different from the flow path 20 of the diffuser portion 19. Therefore, it is possible to prevent the air from being disturbed by the unevenness of the scratch and to prevent the supercharging efficiency from being lowered. Further, since the seal plate 44 is formed by the press-fitting plate 47, the processing cost is reduced by eliminating the screw processing for fixing to the bearing housing 3, and the number of parts is reduced by eliminating the need for assembly by bolts. In addition, the manufacturing cost is reduced.

  Further, an oil sump 40 is constituted by the oil drill 36 and the oil drill counter part 39, and the lubricating oil flowing out from the bearing portion 31 flows into the oil sump 40 and is immediately discharged outside through the oil discharge hole 41. 5 and the oil cutting 36 are rotated at a high speed, the amount of lubricating oil that oozes out from between the oil cutting 36 and the oil cutting counter part 39 to the seal plate 44 side is made small, and the lubricating oil that has oozed out from the bearing part 31. It is possible to prevent oil from leaking to the impeller 6 side through the seal ring 37. Further, the diameter of the hole 46 of the fixed seal plate 45 corresponding to the diameter of the press-fitting plate 47 is a diameter capable of processing the outer periphery 42 of the oil-grinding counter part 39. The lubricating oil that has been formed and flows out from between the oil drill 36 and the oil drill counter part 39 is caused to flow along the outer periphery 42 of the oil counter counter part 39 to prevent the lubricant from moving toward the seal ring 37. be able to. Furthermore, since the diameter of the hole 46 of the fixed seal plate 45 corresponding to the diameter of the press-fit plate 47 is a diameter that allows the oil discharge hole 41 to be processed in the oil cutting counter part 39, the oil cutting 36 and the oil cutting counter part The oil discharge hole 41 is formed in the oil reservoir 40 formed between the portions 39, and the lubricating oil flowing into the oil reservoir 40 is immediately discharged to the outside through the oil discharge hole 41, so that the lubricating oil is directed to the seal plate 44 side. Therefore, it is possible to prevent the lubricating oil from leaking to the impeller 6 side through the seal ring 37.

  In the embodiment of the present invention, the oil sump 40 includes a first projecting portion 36d that projects to the outer periphery at the end of the rear portion 36c of the oil drain 36, and a second projecting portion 36e that projects to the outer periphery at an intermediate position in the axial direction. , Formed by the first pair of flanges 39a formed on the oil drilled pair 39 and opposed to the first projecting part 36d, and the second paired pair 39b formed on the oil drilled pair 39 and opposed to the second projected part 36e. Therefore, the oil sump 40 can be easily formed, and the lubricating oil flowing out from the bearing portion 31 easily flows into the oil sump 40. Therefore, the turbine shaft 5 and the oil drain 36 rotate at a high speed. However, the amount of oil that oozes out from the gap between the oil drill 36 and the oil drill counter part 39 to the seal plate 44 side can be made small, so that the lubricating oil that has flowed out from the bearing section 31 leaks to the impeller 6 side through the seal ring 37. To prevent Can.

  The turbocharger of the present invention is not limited to the above illustrated example, and the form of the bearing portion is not limited to the illustrated example, and may be the configuration of the conventional example or other configurations. Of course, various changes can be made without departing from the scope of the present invention.

It is the schematic which shows the turbocharger as an example which implements this invention. It is the schematic which expands and shows oil cutting and a seal plate. It is the schematic which shows a bearing housing and an oil cutting counter part. It is the schematic which shows the flow path of an oil discharge hole. It is a conceptual diagram which shows the state which forms an oil cutting counter part. It is the schematic which shows the state provided with the oil cutting on the seal plate. It is the conceptual diagram which press-fit the seal plate in the bearing housing. It is the schematic which shows a press-fitting jig. It is the schematic which shows the conventional turbocharger. It is the schematic which expands and shows the conventional oil cutting and a seal plate.

Explanation of symbols

DESCRIPTION OF SYMBOLS 3 Bearing housing 5 Turbine shaft 6 Impeller 31 Bearing part 36 Oil cutting 36a Front part 36c Rear part 36d 1st protrusion part 36e 2nd protrusion part 39 Oil cutting edge part 39a 1st pair collar part 39b 2nd counter part 40 Oil sump 41 Oil Discharge hole 42 Outer periphery 44 Seal plate 47 Press-fit plate

Claims (2)

  A seal plate is disposed between the bearing portion that supports the turbine shaft on the bearing housing and the front impeller and prevents oil leakage from the bearing portion to the impeller side against the outer periphery of the front portion of the oil drain. A turbocharger provided integrally with the bearing housing so as to be positioned on the back surface of the impeller, and further having an oil drainage facing portion formed on the bearing housing so as to constitute an oil sump facing the outer periphery of the rear portion of the oil drilling The seal plate is constituted by a press-fitting plate, and the press-fitting plate has a diameter smaller than the outer diameter of the impeller, and an oil discharge hole provided in the oil-slip counter-toe portion for processing the outer periphery of the oil-slip-to-side counter part. A turbocharger characterized by being equal to or greater than the minimum working diameter for machining. The oil sump is formed at the first protrusion protruding to the outer periphery at the rear end side of the oil drain, the second protrusion protruding to the outer periphery at an axially halfway position, and the first protrusion 2. The turbocharger according to claim 1, further comprising: a first pair of flanges facing each other, and a second counterbore formed on the oil drilling counterspot and facing the second projecting portion.

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