GB2498748A - Impeller to shaft connection system - Google Patents
Impeller to shaft connection system Download PDFInfo
- Publication number
- GB2498748A GB2498748A GB1201278.7A GB201201278A GB2498748A GB 2498748 A GB2498748 A GB 2498748A GB 201201278 A GB201201278 A GB 201201278A GB 2498748 A GB2498748 A GB 2498748A
- Authority
- GB
- United Kingdom
- Prior art keywords
- impeller
- text
- connector body
- shaft
- connection system
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 229910000831 Steel Inorganic materials 0.000 claims description 16
- 239000010959 steel Substances 0.000 claims description 16
- 239000000463 material Substances 0.000 claims description 10
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 11
- 239000004411 aluminium Substances 0.000 description 8
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 8
- 229910052782 aluminium Inorganic materials 0.000 description 8
- 229910000838 Al alloy Inorganic materials 0.000 description 4
- 239000003921 oil Substances 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 238000005755 formation reaction Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- FYYHWMGAXLPEAU-UHFFFAOYSA-N Magnesium Chemical compound [Mg] FYYHWMGAXLPEAU-UHFFFAOYSA-N 0.000 description 1
- 229910000954 Medium-carbon steel Inorganic materials 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000001351 cycling effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 229910052749 magnesium Inorganic materials 0.000 description 1
- 239000011777 magnesium Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
- 230000008646 thermal stress Effects 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/025—Fixing blade carrying members on shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
- F01D5/048—Form or construction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A connection system for connecting an impeller 1 to a shaft 2. The impeller has a shaft-side hub extension H with a central hole. The connection system has a connector body 3 which is inserted into the hole. The connector body has a threaded portion 12 which screws onto a corresponding threaded portion 7 of the shaft such that the connection system provides a rotationally fixed connection between the impeller and the shaft. The connection system further has a split collar 21 which surrounds the connector body, and is frictionally connected on an inner side with an outwardly facing surface 14 of the connector body, and is frictionally connected on an outer side with a radially inner surface of the hub extension. The connection system further has a piston-type ring 22 which is housed in respective recesses formed in the outer side of the split collar and the radially inner surface of the hub extension.
Description
I
I
CONNECTION SYSTEM
Field of the Invention
The present invention relates to a connection system for connecting an impeller to a shaft, and in particular, but not exclusively, for connecting an impeller of a turbocharger to a turbocharger shaft.
Background of the Invention
Turbocharger impellers are typically made of aluminium alloys to provide low rotational inertia with reasonable strength at a commercially-acceptable cost. Attachment of the impeller to the steel turbocharger shaft is achieved in various ways. For example, because of the relative weakness of aluminium and the small diameter of the shaft, one option is to provide the impeller with a steel insert containing a screw-threaded socket which can be threaded onto the shaft. This arrangement can take a higher torque than a connection in which the shaft is directly threaded into the aluminium body (the torque is proportional to the power transmitted across the joint, and so the impeller can be used at a higher pressure ratio than one in which there is a direct threaded connection).
Typically, such an insert is fitted into the impeller by shrink fitting; the aluminium body of the impeller is heated to expand the bore which is to receive the steel insert, while the insert is cooled, for example using liquid nitrogen, before being inserted into the bore. The resultant interference connection is restricted by the temperature to which the aluminium can be heated before its material properties are affected, and by the temperature to which the steel can be cooled.
While the arrangement described can perform satisfactorily, a problem can arise during cycling of the turbocharger from rest to full load. As the turbocharger starts to spin, the joint is affected by centrifugal forces, whereby the aluminium grows outwards away from the steel insert. This reduces the interference force between the insert and the impeller, and due to design constraints it has been found that this reduction tends to be greater at one end of the insert than at the other. Consequently, the insert is gripped more firmly at one of its ends than at the other. The turbocharger then starts to heat up, and because of the different thermal coefficients of expansion of the aluminium alloy and the steel, the aluminium grows So axially more than the steel, causing the two metals to slide over each other, except at the location where the impeller still grips the insert firmly. On shutdown, the centrifugal stresses are removed, but the thermal stresses remain for some minutes as the turbocharger cools.
In this process, the point of grip of the impeller on the insert changes from one end to the other, and as the turbocharger cools, the insert "walks' along the impeller.
In certain very cyclic conditions (for example fast ferry applications in high ambient temperatures), it has been observed that the insert can move so far along the impeller that turbocharger failure can occur. Although the effect can be mitigated to some degree by increasing the original interference between the components, for the reasons mentioned above this solution is limited, and it is therefore desirable to achieve a design which ensures that the point of grip remains at the same location during the operating cycles, rather than shifting from one end of the insert to the other.
Accordingly, EP1 394387 proposes an outer steel constraining ring which reinforces the frictional contact between aluminium impeller and the insert. Since the ring does not expand as much as the impeller body as the turbocharger heats up, the point of grip between the impeller and the insert remains within the axial extent of the ring during the whole operating cycle of the turbocharger, thereby preventing the tendency of the impeller to "walk" along the insert. As a consequence, the operating life of the turbocharger can be considerably extended in comparison with the conventional turbocharger without the constraining ring.
However, the assembly of such a joint is relatively complex. First the insert and impeller bore are manufactured to tight tolerances. Then typically the insert is cooled and the impeller heated, and the insert is placed within the impeller bore at a hub extension of the impeller. As the insert warms up and the impeller cools, a shrink fit joint is formed, but because of the non-axisymmetrical shape of the impeller1 some distortion occurs within the impeller. Generally, the outer surface of the impeller hub extension must therefore be reground to be axisymmetric so that it will be suitable for the outer joint with the constraining ring. A further ring may then be shrunk onto a flange portion of the insert to prevent the constraining ring from coming off the impeller.
Summary' of the Invention
It would be desirable to provide a connection between an impeller and a shaft which can transmit high torques but has little or no susceptibility to the "walking".
Accordingly, in a first aspect the present invention provides a connection system for connecting an impeller to a shaft, the impeller having a shaft-side hub extension with a central hole, wherein the connection system has: a connector body which is inserted into the hole, the connector body having a threaded portion carrying a thread which screws onto a corresponding threaded portion of the shaft such that the connection system provides a rotationally fixed connection between the impeller and the shaft; a split collar which surrounds the connector body and which is frictionally connected on an inner side with an outwardly facing surface of the connector body and is frictionally connected on an outer side with a radially inner surface of the hub extension, the frictional connections transmitting torque between the shaft and the impeller; and a piston-type ring which is housed in respective recesses formed in the outer side of the split collar and the radially inner surface of the hub extension.
The split collar can be formed of a material having a coefficient of thermal expansion which is similar to that of the connector body. In this way, the differential thermal forces which drive walking" can be reduced or eliminated across the interface between the connector body and the split collar, Meanwhile, the piston-type ring provides resistance to relative axial thermal movement across the interface between the impeller and the split collar. Thus the connection system can eliminate "walking" of the impeller relative to the connector body while maintaining a joint that is capable of transmitting high torques. In addition, regrinding of the outer surface of the impeller hub extension can be avoided.
A second aspect of the invention provides an impeller having a shaft-side hub extension with a central hole and filled with a connection system according to the first aspect, the connector body being joined to the hub extension by the split collar and the piston-type ring.
A third aspect of the invention provides the impeller fitted with a connection system of the second aspect, which impeller is connected to a shaft having a corresponding threaded section, the thread of the threaded portion of the connector body screwing onto the corresponding threaded portion of the shaft.
A fourth aspect ol the invention provides a turbocharger having the connected impeller and shaft of the third aspect.
Optional features of the invention will now be set out. These are applicable singly or in any combination with any aspect of the invention.
The central hole may be a blind hole (i.e. with an end surface). Thus, the impeller may not have a through-hole extending from one side to another of the impeller.
The threaded portion of the connector body is typically within the central hole. In this way, an axially compact arrangement can be achieved.
Preferably, the frictional connections transmit substantially all of the torque between the shaft and the impeller.
To provide the rotationally fixed connection, the threads can be positive-locking, e.g. tapered.
However, another aption is for the connector body to have an abutment surface which engages a corresponding abutment surface of the shaft when the thread portions are screwed together, thereby tightening the threads to provide the rotationally fixed connection.
The outwardly facing surface of the connector body may be approximately cylindrically shaped. The radially inner surface of the shaft-side hub extension of the impeller may be correspondingly approximately cylindrical.
The frictional connection between the connector body and the split collar can be achieved by e.g. press fitting or shrink fitting the connector body into the split collar. Prior to the fitting of the connector body into the split collar, the split collar and the piston-type ring can be mounted into the central hole such that, when the frictional connection between the connector body and the split collar is achieved, the split collar is urged outwardly to simultaneously achieve the frictional connection between the split collar and the hub extension.
The connector body can be of cup-like shape and can have a flange portion around the mouth of the cup which, when the connector body is inserted into the central hole, engages a shaft side end face of the hub extension.
The connector body may be formed of a material having a greater strength Ihan the material of the impeller. For example, the shaft can be formed of steel (e.g. a high strength steel), and the impeller can be formed of aluminium alloy. The connector body can also be formed of steel (e.g. a high strength steel). The split collar is preferably formed of a material having about the same coefficient of thermal expansion as the material of the connector body. Thus the split collar can also be formed of steel (e.g. a high strength steel).
The connector body and/or the impeller may have one or more centring portions having respective engagement surfaces which engage with one or more corresponding centring portions of the shaft, the threaded portion of the connector body and the centring portions of the connector body and/or the impeller being distributed along the impeller axis. The thread s surface of the connector body and the engagement surfaces of the connector body and/or the impeller can face radially inwardly, and the respective diameters on the shaft of the thread and the engagement surfaces can then decrease towards the impeller.
Generally the impeller has a casing, and the connector body and/or the hub extension can then form a seal with a section of the casing. For example, the seal can include a sealing io ring, which may be carried by the casing section and which may be received by a corresponding circumferential recess formed on an outer surface of the connector body and/or the hub extension. The sealing ring may have one or more annular grooves on its radially inner face, and the recess may have corresponding circumferential ribs which are received in the grooves. Another option is for the seal to include a labyrinth seal, with is formations on facing surfaces of the casing section and the connector body and/or the hub extension forming the labyrinth.
The connector body may be formed with or may carry a circumferential oil thrower formation at its radially outer surface.
Further optional features of the invention are set out below.
Brief DescriDtion of the Drawings Embodiments of the invention will now be described by way of example with reference to the accompanying drawings in which: Figure 1 shows (a) a sectional elevation, and (b) a cross section on plane A-A through a turbocharger impeller joined to a shaft by a connection system in accordance with an embodiment of the invention; Figure 2 is a close-up schematic view of a seal between a section of a casing of the impeller of Figure 1 and a hub extension of the impeller; Figure 3 is a close-up schematic view of a seal between a section of a casing of an impeller and a sleeve portion of a further embodiment of the connection system; and Figure 4 shows schematically a sectional elevation of a further embodiment of the connection system.
Detailed Description and Further Optional Features of the Invention Figure 1(a) is a sectional elevation through an aluminium alloy turbocharger impeller 1 joined s to a steel turbocharger shaft 2 by a connection system in accordance with an embodiment of the invention. Figure 1(b) is a cross-section along the plane A-A of Figure 1(a). The connection system includes a connector body 3 and a split collar 21 located at a hub extension Hon the shaft side of the body of the impeller 1. The alloy of which the impeller is made (known in the U.S.A. by the designation "2618k') has a relatively high strength for use up to a temperature of about 200°C, having a composition of aluminium with about 2.5wt.% copper and smaller amounts of magnesium, iron and nickel. The material of the connector body 3 and the split collar can be medium carbon steel such as EMS.
The connector body 3 is of cup-like shape and has a threaded portion 12 with a threaded bore 11 forming the base of the cup, and a flange portion B around the mouth of the cup.
The split collar 21 can be in two pieces and surrounds a radially outer surface 14 of the connector body 3.
To join the connector body 3 to the impeller 1, firstly a piston-type ring 22 is compressed to allow it to be fitted in a corresponding recess formed in a radially inner surface of the hub extension H. The split collar 21 is loosely mounted inside the hub extension H such that an outer side of the collar 21 opposes a radially inner surface of the hub extension H, with the ring 22 being received in a matching recess formed in that outer side. Typically, the ring 22 is located at between about one third and two thirds along the axial length of the hub extension H. The connector body 3 is then fitted to the hub extension H by cooling the connector body 3 to cause it to shrink and by heating the impeller ito cause the hub extension H to expand, and then inserting the connector body 3 into the collar 21 until the flange portion 8 contacts the end face G of the hub extension H to determine the relative axial positions of the connector body 3 and the hub extension H. The threaded portion 12 of the connector body 3 has a small clearance from the end of the recess. On returning from their thermal excursions, the connector body 3 and collar 21 frictionally grip across the outwardly facing surface 14 of the connector body 3 and the inner side of the collar 21, and likewise the hub extension H and the collar 21 (which is urged radially outwardly by a combination of the physical insertion and re-warming of the connector body 3) frictionally grip across the radially inner surface of the hub extension H and the outer side of the collar 21 The shaft 2 is formed at its end with a shoulder 4 surrounding a cylindrical centring portion 5, and a screw-threaded portion 7 of further reduced diameter extending from The end of the s centring portion. After the connector body 3 is fitted to the hub extension H, the screw-threaded portion 7 of the shaft 2 is screwed into the bore 11 of the threaded portion 12 of the connector body 3, the centring portion S of the shaft being received in a corresponding centring portion 10 of the connector body 3 in a close, but not tight, fit to ensure the shaft 2 aligns with the axis of the impeller 1. The threads are screwed until the shoulder 4 of the io shaft 2 engages with flange portion 8, which causes the threads to tighten and provides a rotationally fixed connection between the impeller 1 and the shaft 2.
The outer diameter of the flange portion 8 of the connector body 3 is provided with an oil capture/thrower ring ft which in this embodiment of the invention is machined into the flange portion 8. Another option, however, is to form the ring R as a separate component.
As shown better in Figure 2, a section 15 of the impeller casing and the outer surface of the hub extension H are in close proximity to help provide a rotating oil and pressure seal between the impeller I and the casing. To improve the seal, the hub extension H has a recess 13 on its outer surface which is bounded at one end by the flange portion 8 connector body 3 and which receives a sealing ring 16 carried by the casing section 15. To reduce wear between the sealing ring 16 and the hub extension H, the casing section 15 has a small abutment surface 20 on the shaft side (right hand in Figure 1) of the seal ring 16 and against which the sealing ring 16 rests. To provide enhanced sealing, the sealing ring 16 has annular grooves 18 on its radially inner face, and the recess has corresponding circumferential ribs 17 which are received in the grooves, as described in EPA 1130220.
Alternatively, however, the sealing ring can be a plain ring (i.e. without grooves) received in a plain recess (i.e. without ribs). The sealing ring 16 co-operates with the casing section 15 and serves to retain lubricating oil to the shaft side of the assembly and compressed air to the impeller side of the assembly (left hand in Figure 1). The compressed air is contained between the body of the impeller 1, the hub extension H with its sealing ring 16, and the impeller casing, within which the impeller assembly is mounted for rotation on overhung bearings (not shown).
B
By forming the split collar 21 from the same material as that of the connector body 3, the differential thermal forces which drive "walking" are substantially eliminated across the interface between the connector body 3 and the split collar 21. In contrast, across the interface between the impeller 1 and the split collar2l, such forces do exist, but the piston-type ring 22 provides resistance to relative axial thermal movement. Further, by containing the threaded connection between the connector body 3 and the shaft 2 in the central hole of the hub extension H, an axially compact arrangement is achieved. In addition, as there is no need to fit a constraining ring of the type described in EP1 394387 to the hub extension H, regrinding operations can be avoided during fitting of the connector body 3.
Figure 3 is a close-up schematic view of a seal between a section of a casing of an impeller and the flange portion B of a further embodiment of the connector body 3. In this case, instead of a seal formed by a sealing ring, the hub extension H and flange portion B on one side and the casing section 15 on the other side have engaging surfaces 19 carrying respective sets of machined grooves which interlock to form a labyrinth seal.
Figure 4 shows schematically a sectional elevation of a further embodiment of the connection system. This embodiment is similar to the embodiment of Figure 1 except that the shaft 2 has two centring portions 5a, Sb, and the connector body has two corresponding centring portions ba, 1gb. The threaded portions?, 12 of the shaft 2 and the connector body are located axially between the engaging pairs of centring portions such that, on each of the shaft 2 and the connector body 3, the respective diameters of the threaded portions and the centring portions decrease towards the impeller. A further difference relative to the previous embodiments is that the threads are tapered, so that merely screwing the threaded portions 7, 12 together results in a rotationally fixed connection between the impeller 1 and the shaft 2.
While the invention has been described in conjunction with the exemplary embodiments described above, many equivalent modifications and variations will be apparent to those skilled in the art when given this disclosure. For example, in embodiments such as that of Figure 4, instead of the connector body having a centring portion 1 Oa, the impeller may have a centring portion at the base of the recess that engages with the centring portion 5b of the ao shaft. Accordingly, the exemplary embodiments of the invention set forth above are considered to be illustrative and not limiting. Various changes to the described embodiments may be made without departing from the spirit and scope of the invention.
All references referred to above are hereby incorporated by reference.
Claims (1)
- <claim-text>CLAIMS1. A connection system for connecting an impeller (1) to a shaft (2), the impeller having a shaft-side hub extension (H) with a central hole, wherein the connection system has: a connector body (3) which is inserted into the hole, the connector body having a threaded portion (12) carrying a thread which screws onto a corresponding threaded portion (7) of the shaft such that the connection system provides a rotationally fixed connection between the impeller and the shaft; a split collar (21) which surrounds the connector body and which is frictionally connected on an inner side with an outwardly facing surface (14) of the connector body and is frictionally connected on an outer side with a radially inner surface of the hub extension, the frictional connections transmitting torque between the shaft and the impeller; and a piston-type ring (22) which is housed in respective recesses formed in the outer side of the split collar and the radially inner surface of the hub extension.</claim-text> <claim-text>2. A connection system according to claim 1, wherein the material of the split collar has about the same coefficient of thermal expansion as the material of the connector body.</claim-text> <claim-text>3. A connection system according to claim 1 or 2, wherein the split collar and the connector body are formed of steel.</claim-text> <claim-text>4. A connection system according to any one of the previous claims, wherein the frictional connections transmit substantially all of the torque between the shafi and the impeller.</claim-text> <claim-text>5. A connection system according to any one of the previous claims, wherein the central hole is a blind hole.</claim-text> <claim-text>6. A connection system according to any one of the previous claims, wherein the connector body and/or the impeller have one or more centring portions having respective engagement surfaces which engage with one or more corresponding centring portions of the shaft, the threaded portion of the connector body and the centring portions of the connector body and/or the impeller being distributed along the impeller axis.</claim-text> <claim-text>7. A connection system according to any one of the previous claims, wherein the impeller has a casing, and the connector body and/or the hub extension forms a seal with a section of the casing.</claim-text> <claim-text>8. A connection system according to any one of the previous claims, wherein the connector body is formed with or carries a circumferential oil thrower formation at its radially outer surface.</claim-text> <claim-text>9. An impeller having a shaft-side hub extension with a central hole and fitted with a S connection system according to any one of the previous claims, the connector body being joined to the hub extension by the split collar and the piston-type ring.</claim-text> <claim-text>10. The impeller fitted with a connection system of claim 9, which impeller is connected to a shaft having a corresponding threaded section, the thread of the threaded portion of the connector body screwing onto the corresponding threaded portion of the shaft.</claim-text> <claim-text>11. A turbocharger having the connected impeller and shaft of 10.</claim-text>
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1201278.7A GB2498748B (en) | 2012-01-24 | 2012-01-24 | Connection system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1201278.7A GB2498748B (en) | 2012-01-24 | 2012-01-24 | Connection system |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB201201278D0 GB201201278D0 (en) | 2012-03-07 |
| GB2498748A true GB2498748A (en) | 2013-07-31 |
| GB2498748B GB2498748B (en) | 2017-07-26 |
Family
ID=45840958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB1201278.7A Active GB2498748B (en) | 2012-01-24 | 2012-01-24 | Connection system |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2498748B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58220901A (en) * | 1982-06-15 | 1983-12-22 | Nissan Motor Co Ltd | Installing structure of impeller onto ceramic shaft |
| US4915589A (en) * | 1988-05-17 | 1990-04-10 | Elektroschmelzwerk Kempten Gmbh | Runner with mechanical coupling |
-
2012
- 2012-01-24 GB GB1201278.7A patent/GB2498748B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58220901A (en) * | 1982-06-15 | 1983-12-22 | Nissan Motor Co Ltd | Installing structure of impeller onto ceramic shaft |
| US4915589A (en) * | 1988-05-17 | 1990-04-10 | Elektroschmelzwerk Kempten Gmbh | Runner with mechanical coupling |
Also Published As
| Publication number | Publication date |
|---|---|
| GB201201278D0 (en) | 2012-03-07 |
| GB2498748B (en) | 2017-07-26 |
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| 732E | Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977) |
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